EP2389463B1 - Drive apparatus for the draw-off rolls of a combing machine - Google Patents

Description

The invention relates to a drive device for generating a pilgrim movement for the tear-off rollers of a comber according to the preamble of claim 1.

For the tear-off and soldering process in a combing machine, the tear-off rollers perform a pilgrim step movement. In other words, before a further tear-off operation, the already formed nonwoven fabric is returned by a certain amount in the direction of the nipper unit in order to connect a new fiber package to the end of the nonwoven fabric. This requires a very special drive to produce such a pilgrim movement for the Abreisswalzen. Here, the Abreisszeitpunkt the new fiber package, as well as the tear rate of Abreisswalzen tune exactly to the forceps and circular comb movement to obtain a desired solder joint, or to obtain a qualitatively uniform nonwoven fabric.

In the DE-PS 1 685 575 an embodiment has been described, wherein this movement is generated using a differential gear. In this case, the web of the differential gear, in which the sun gears are rotatably mounted, driven by a uniformly driven gear which is in driving connection with a web wheel connected to the web. The gear sits in the present case against rotation on the drive shaft of the circular comb. In the driven web a plurality of planet gears are rotatably mounted, which are in engagement with the respective sun gear. An eccentric drive communicating with a lever gear transmits non-uniform motion to the differential gear axis and thus to a first sun gear connected thereto. About this non-uniform motion, the previously described uniform drive movement is superimposed and generates the desired pilgrim movement for the Abreisswalzen. This gear design has proven itself for many years, but requires a complex and stable design to absorb the resulting high acceleration forces can. In addition, friction forces are present at each of the joints within the lever mechanism, through which the required power must be increased. at ever higher demands on the Kammspielzahlen are at some point reached the limits of the capacity of this gear design. In addition, the degree of freedom in the design of the movement curve of the Abreisswalzen is limited by the use of the known lever mechanism.

There have also been other proposals made to realize the pilgrim movement with other means and gear units. On the one hand, it has been proposed to drive the tear-off rollers directly via one or more electric motors. Such a solution is z. B. from the EP-374 723 refer to. Furthermore, from the U.S. Patent 3,604,063 a variable transmission unit is known, wherein special cam and cam gear units are used to achieve the desired pilgrim step movement.

From the U.S. Patent 1,818,555 an embodiment is known wherein a constant rotational movement of a drive axle is converted into a pilgrim movement using a differential gear with non-circular gears. This Pilgerschrittbewegung is transmitted via a, connected to a sun gear output shaft and a subsequent gear stage on the Abreisswalzen. Furthermore, in the published CN 200710022458.7 a device has been described, and equivalent to the cited US'555, the use of a differential gear with gear stages with non-circular gears is proposed. The only difference to the US'555 is only that the drive of the web takes place via an outer web wheel, while in the solution of US'555 the drive of the web takes place via a central shaft.

Although in the described solutions of US'555 and CN'458.7 a corresponding pilgrim step movement can be achieved on the basis of the gear stages used with non-circular gears, however, such a solution is limited in the transferability of high powers and thus high torques, since it is not mechanically it is possible to use more than one planetary gear. In addition, the adjustability of the drive movement of the tear-off rollers in contrast to the solution according to the already described U.S. Patent 1,818,555 limited.

The invention now has the task to improve the known solutions and to propose a device for driving the Abreisswalzen, which on the one hand, a reduction of the previously required torques (benefits) includes while increasing the degree of freedom in the design of the movement curve of Abreisswalzen. Ie. It is thus intended to achieve an optimized movement curve of the tear-off rollers with lower torque loads.

This object is achieved by proposing that the drive unit for the sun gear of the first gear stage of the differential gear is formed of a gear stage with non-circular gears, which converts a uniform rotational movement of a main drive in a non-uniform rotational movement. The proposed use of a transmission with a gear stage with non-circular gears, instead of the known use of a lever mechanism in conjunction with a Exzentantrieb, it is possible to maintain a previously proven per se drive structure. At the same time achieved with the proposed use of the gear stage with non-circular gears previously unknown optimization possibilities with respect to the reduction of the drive load and with respect to the adjustment of the movement curve of the Abreisswalzen.

Furthermore, it is proposed that the drive element for the web consists of a drive shaft on which a fixed gear, which is directly or indirectly in drive connection with a web wheel of the web of the differential gear. The term "indirectly" can z. As an intermediate fall, which is interposed between the gear shaft fixed to the drive shaft and the web to z. B. to transmit a required direction of rotation to the web wheel.

In this case, the drive shaft may have a further drive wheel, which is in drive connection with a drive element of the main drive, which is also in drive connection with the gear stage with non-circular gears. Thus, the synchronization of the two drive paths is ensured, since both are removed from the same drive element of the main drive, without further drive elements are interposed.

Furthermore, it is proposed that the drive element of the main drive consists of a rotatably mounted in the machine frame gear, which is driven by other means of a central drive motor (main drive), wherein the axis of rotation of the gear is coaxial with the input shaft of the gear stage with the non-circular gears and the further drive wheel of the drive shaft is designed as a gear which is in drive connection with the gear of the main drive. However, it is also an embodiment conceivable in which the gear of the main drive is mounted directly on the input shaft of the gear stage with the non-circular gears.

To obtain an adjustment, in particular for adjusting the Abreisszeitpunktes of the Abreisswalzen against the forceps movement is proposed that the input shaft of the gear stage is connected via releasable fasteners rotatably connected to the gear of the main drive.

The fastening means can be provided with guides which allow an adjustment of the angle of rotation between the input shaft and the gear of the main drive with dissolved fasteners. Thus, it is possible to move the cycle of movement of the tear-off against the forceps movement. The drive of the pliers is also coupled to the main drive.

A displacement of the movement cycle of the Abreißwalzen can alternatively be achieved if the gear on the drive shaft via fasteners releasably secured and the angular position between the drive shaft and the gear via means is adjustable.

To adjust the movement cycle of Abreisswalzen may alternatively be used another embodiment, it being proposed to releasably fix the web wheel on the web (2) of the differential gear (1) via means (13) and - seen in the circumferential direction of the web (2) - Provide adjustable relative to the web in its angular position via adjusting means (12, 14).

Further advantages of the invention will be shown with reference to the following embodiments and described in more detail.

Fig. 1

eine schematische Schnittdarstellung einer erfindungsgemäss ausgebildeten Vorrichtung

Fig.2

eine Seitenansicht X nach Fig.1auf das Getriebe mit unrunden Zahnrädern

Fig.3

eine vergrösserte Teilansicht nach Fig.1 mit einem Beispiel für die Befestigung und Verstellung für das Stegrad des Differentialgetriebes

Fig.4

eine Ansicht A nach Fig.1 auf das Antriebsrad 18

Fig.5

eine Seitenansicht Y nach Fig.1 auf das Differentialgetriebe

Fig.6

ein Diagramm mit einem Kurvenverlauf der Abreisswalzenbewegung während eines Kammspieles

Fig.7

ein Diagramm mit der Drehmomentbelastung des Antriebes für die Abreisswalzen während eines Kammspieles

Show it:

Fig. 1

a schematic sectional view of an inventive device

Fig.2

a side view X after Fig.1 on the gearbox with non-circular gears

Figure 3

an enlarged partial view Fig.1 with an example of the attachment and adjustment for the web gear of the differential gear

Figure 4

a view A after Fig.1 on the drive wheel 18th

Figure 5

a side view Y after Fig.1 on the differential gear

Figure 6

a diagram with a curve of the Abreisswalzenbewegung during a comb play

Figure 7

a diagram with the torque load of the drive for the Abreisswalzen during a comb play

Fig. 1 shows a differential gear 1 with a circumferential ridge 2, which is rotatably mounted on one side on the bearing 6. The bearing 6 is supported on a central shaft 5, which is rotatably mounted in the present case on the bearings 10, 11 in the machine frame MS. On the other side of the web 2 is rotatably mounted on a bearing 7. The bearing 7 is supported on a hollow shaft 9, which is supported on the schematically indicated bearings 8 on the already cited shaft 5. Of course, a variety of other storage options would be conceivable. The circumferential web 2 is provided with a web wheel 3, which is fixedly connected to the web. Another alternative is shown in an enlarged view Fig. 3 shown, wherein the web wheel 3 is provided with a superior base body 12. At the web-projecting part of the base body 12 longitudinal slots 14 are provided on both sides whose longitudinal extent in the circumferential direction of the web 2 extends. Through these slots 14 in each case one or more screws 13, which are fastened in threaded bores 15 of the web 2. By tightening the screws 13, the web wheel 3 is fixed relative to the web 2. After loosening the screws 13, of which there are several distributed on the circumference of the web 2, the web wheel can be rotated relative to the web by an amount in the circumferential direction, whereby its angular position relative to the web changed. As a result, adjustments with respect to the position of the tear-off Abreisswalzen the nipper unit (not shown) possible. This will be described later in more detail.

With the web wheel 3 is via an intermediate gear 37, a gear Z in engagement and in drive connection. As indicated schematically, the intermediate wheel 37 is mounted rotatably in the machine frame via its axis 36 in bearings L. The gear Z is rotatably mounted on a, mounted on bearings L in the machine frame drive shaft 20. At a distance from the gear Z, a further gear 16 is mounted on the drive shaft 20, which is in drive connection with a gear 18 of a main drive HA. In this case, via the mounted on the axis 48 in the bearing Lx in the machine frame gear 18 is driven by a gear 19 which is connected via a shaft 38 to a central gear unit G in drive connection. The drive of the transmission unit G is carried out by a motor M via the drive connection 40 shown schematically. Of course, this is only one of many possible variants of the drive. For example, it is also conceivable to provide belt drives instead of the gear pairs shown.

Alternatively to the in Fig. 3 adjustment shown can also be provided an adjustment, as z. In Fig. 1 will be shown. In this case, the gear Z is connected to a hollow shaft 22, which has a flange 23 and extends coaxially to the drive shaft 20. The flange 23 is opposite to a flange 25, which is also coaxial with the shaft 20 and rotatably connected to the shaft 20 via a spring 28 which projects into a groove 29 of the shaft 20. In order to prevent an axial displacement of the flange 25, the flange is secured by a screw 27 indicated schematically. Via the screw connection 24 shown schematically, both flanges 23, 25 are fixed against each other. Thus, the gear Z is fixed in rotation on the shaft 20. As in Fig. 5 (View Y after Fig.1 ), in each case a slot 30 is provided in the region of the screw connection 24, via which, after the screw connection 24 has been released, a change in the angular position between the gear Z and the shaft 20 can be performed. Even with this device, a shift of the Abreisszeitpunktes the Abreisswalzen to the position of the nipper unit is possible.

The drive of the Abreisswalzen A1, A2 on the one hand via the uniformly driven gear Z, via the intermediate gear 37, the web wheel 3 of the web 2 in Rotated motion offset. As a result of this rotational movement, the bearing receivers L1 to L6 connected to the web 2 are also moved, in which the planetary gears U1 to U6 are rotatably mounted via the shafts 33, 34, 35. The planetary gears U1 to U3 (see Fig.1 ) with the sun gear S1 in drive connection, which is rotatably mounted on the shaft 5.

The sun gear S2 of the second gear stage G2 of the differential gear 1 is fixedly connected to a rotatably mounted hollow shaft 9, which, as already described, is supported on the rotatably mounted shaft 5 via the bearings 8. With the sun gear S2 are distributed on its circumference and stored in the web 2 planet gears U4 to U6 in drive connection. The planetary gears U4 to U6 are connected via the shafts 33,34,35 with the planetary gears U1 to U3.

At the opposite end of the hollow shaft 9, a gear Z1 is fixed, which in turn is in drive connection with the gears Z2 and Z3. The gears Z2, Z3 are connected via the shafts W1, W2 with the Abwalwalzen A1, A2. The tear-off rollers A1, A2, or the shafts W1, W2 are mounted on the schematically indicated bearings L in the machine frame MS:

The shaft 5, on which the sun gear S1 is mounted, is at the same time the output shaft of a transmission stage G3, which is connected upstream of the differential gear 1, with non-circular gears 43, 44, which engage with one another within a housing 4. The non-circular gear 43 is rotatably mounted on the shaft 5. The non-circular gear 42 is rotatably mounted on a shaft 44 on which at its other end a flange 50 is fixed, via which it is fixedly connected via screws 51 to the gear 18 of the main drive HA. The shaft 44 is, as indicated schematically, rotatably supported by the bearing 45 in the machine frame MS. Of course, even more bearings can be provided.

Similarly, bearings for the shafts 5 and 44 are provided within the housing 4, which in the Fig.1 was indicated schematically.

The screws 51 project through slots 53 of the flange 50 (see Fig. 4 View A of Fig.1 ), and are received in threaded holes 55 which are provided in the gear 18. The gear 18 is rotatably supported via the bearing Lx in the machine frame via the axis 48. The axes of rotation of the shaft 44 and the axis 48 are parallel to each other axially. The uniform drive of the Gear 18 is, as already described, via the gear 19, which is connected via the shaft 38 with a gear G, which is driven by the drive motor M at a uniform speed.

Instead of already in Fig. 3 and Fig. 5 shown adjustment devices may be provided for adjusting the movement curve of the Abreisswalzen as in Fig. 4 is shown. After loosening the screws 51, the flange 50 can be rotated about the slots 53 by a certain angle of rotation to be fixed in this new position again by tightening the screws 51. Between the flange and the gear 18 markings may be provided (not shown) via which a corresponding adjustment can be determined. With this adjustment, the movement curve of the Abreiszylinder against the movement curve of the nipper unit, which is also driven by the main drive HA, be moved.

Such a movement curve of the Abreisswalzen is z. In Fig. 6 shown, which represents over the course of a comb play KS. In the first area, the tear-off rollers perform a backward movement, as a result of which the already formed nonwoven fabric is returned in the direction of the nipper unit. Then, a reversing movement and the Abreisswalzen move forward to perform the Abreisvorgang. The amount exceeding the zero line then constitutes the actual delivery amount of the fiber fleece.

By this adjustment, in particular the tear-off time of the tear-off rollers A1, A2 can be varied.

About the gear stage G3 with the non-circular gears 42, 43, the gear 18 via 44 removed uniform rotational movement is transmitted to the non-circular gear 42. This is converted in cooperation with the engaged non-circular gear 43 in the gear stage G3 in a non-uniform rotational movement, which is transmitted via the shaft 5 to the sun gear S1.

At the same time is also transmitted from the gear 18 from a uniform rotational movement via the gear 16 to the shaft 20 and thus to the gear Z.

The gear Z transmits this uniform rotational movement via the intermediate gear 37 and the web wheel 3 on the web 2 of the differential gear 1, whereby the planetary gears U1 to U3 are moved about the sun gear S1. This creates a resulting non-uniform rotational movement of the planet gears U1 to U3, which transmit them to the planetary gears U4 connected to them U6. The planet gears U4 to U6 transmit the thus generated non-uniform movement (pilgrim step movement) on the sun gear S2, which transmits them via the shaft 9 and the gear Z1 to the gears Z2 and Z3 of the Abreisswalzen.

By the corresponding design of the non-circular gears 42, 43 of the gear stage G3, it is possible the course of the movement curve ( Fig. 6 ) To optimize the Abreisswalzen so that the drive load, and the applied torques can be significantly reduced, as shown schematically in the diagram of Fig. 7 will be shown. The course of the torques M (Nm) is shown by a comb play, which is divided into 40 index. The drawn with a solid line curve shows the course of the existing torques of previous drive solutions. The dashed curve shows the torque curve, which was achieved under the claim claimed in the invention using the drive unit with non-circular gears. Thus, the torque loads on the positive, as well as on the negative side can be significantly reduced. This results in a lower load on the drive elements and also allows an increase in Kammspielzahl without overloading of the mechanical elements.

By using such a gear stage with non-circular gears for the non-uniform drive of the first sun gear of the differential gear, it is possible to create optimal drive criteria by the free design option in this gear stage to get the benefits already described.

Claims (8)

1. A drive apparatus for generating a pilgrim step motion for the detaching rollers (A1, A2) of a combing machine which rolls are connected via drive means (Z1 - Z3) to an output shaft (9) of a differential gear (1), the rotatably mounted web (2) of which is driven by at least one drive element (20, Z) driven at a constant rotational speed, wherein the differential gear (1) has a second gear stage (G2) which consists of a sun wheel (S2) which is non-rotatably fastened on the output shaft (9) and planet wheels (U4 to U6) which are rotatably mounted in the web (2) via shafts (33 to 35), and a first gear stage (G1) is provided which has planet wheels (U1 to U3) each of which is arranged coaxially to the planet wheels (U4 to U6) of the second gear stage (G2) and non-rotatably fastened on their shafts (33 to 35) and are in drive connection with a further sun wheel (S1) which is non-rotatably fastened on a rotatably mounted drive shaft (5) which is driven by a drive unit (4, G3) with a non-uniform rotational movement, characterized in that the drive unit is formed from a gear stage (G3) having non-circular gear wheels (42, 43) which transforms a uniform rotational movement of a main drive (HA) into a non-uniform rotational movement.
2. The drive apparatus according to claim 1, characterized in that the drive element for the web (2) consists of a drive shaft (20) on which a gear wheel (Z) is non-rotatably fastened which is indirectly or directly in drive connection with a web wheel (3) of the web (2) of the differential gear (1).
3. The drive apparatus according to claim 2, characterized in that the drive shaft (20) has a further drive wheel (16) which is in drive connection with a drive element (18) of a main drive (HA) and which at the same time is also in drive connection with the gear stage (G3) having non-circular gear wheels (42, 43).
4. The drive apparatus according to claim 3, characterized in that the drive element of the main drive (HA) consists of a gear wheel (18) which is rotatably mounted in a machine frame (MS) and is driven via further means (19, 38, G, 40) by a central drive motor (M), wherein the rotational axis (48) of the gear wheel (18) extends coaxially to the intake shaft (44) of the gear stage (G3) having the non-circular gear wheels (42, 43) and the further drive wheel of the drive shaft (20) is formed as gear wheel (16) which is in drive connection with the gear wheel (18) of the main drive (HA).
5. The drive apparatus according to claim 4, characterized in that the intake shaft (44) of the gear stage (G3) having the non-circular gear wheels (42, 43) is non-rotatably connected via detachable fasteners (24) to the gear wheel (18) of the main drive (HA).
6. The drive apparatus according to claim 5, characterized in that in the region of the fasteners (24), guides (30) are provided which allow a displacement of the rotation angle between the intake shaft (44) and the gear wheel (18) of the main drive (HA) when the fasteners (24) are untightened.
7. The drive apparatus according to claim 2, characterized in that the gear wheel (Z) is detachably fastened via fasteners (22, 23, 24) on the drive shaft (20) and the angular position between the drive shaft (20) and the gear wheel (Z) is adjustable via means (30, 24).
8. The drive apparatus according to claim 2, characterized in that the web wheel (3) is detachably fastened via means (13) on the web (2) of the differential gear (1) and - viewed in the circumferential direction of the web (2) - is adjustable via adjusting means (12, 14) in its angular position with respect to the web.

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