CN1138027C - Nipper mechanism of combing machine - Google Patents

Abstract

A combing machine having a swingable nipper set (6, 8, 9, 10) connected to a driving device, the nipper set comprising a lower nipper frame (6) and an upper nipper swingably connected thereto Plate arms (10), the latter are respectively hinged on an elastic column (12) that can swing around the axis (A). The invention finds a simple and inexpensive way to achieve a synchronized movement sequence of the parts as well. At least one transmission stage (20) with non-circular gears (16, 19) is assigned to the shaft (A) on which the elastic column (12) is pivotally articulated, for moving this shaft (A).

Description

Combing machine nipper

technical field

The invention relates to a combing machine, which has a nipper group connected to a drive device, which includes a lower nipper frame and an upper nipper arm connected to it in a swingable manner, the latter being respectively hinged on An elastic column that can swing around an axis.

This arrangement ensures that the upper nipper is lifted from the lower nipper during the combing separation process when the nipper group is in the front position. Once the nipper reaches the rear position, the upper nipper presses against the cotton inlet of the lower nipper under the elastic force of the elastic column, and clamps the lap passing through this area in this position. The fiber tufts protruding from the nipper set in this clamping position are combed out by means of a circular comb located below the nipper. The clamping force acting on the fibers must be as gentle as possible during this process to avoid damage. In addition, it is necessary to apply sufficient clamping force in order to obtain a uniform carding of the fiber bundles as seen along the width of the nipper set.

Background technique

In the hitherto known machine (carding machine E7/6 of Rieter's machine-building plant), one end of the elastic column is supported on an eccentric wheel, the drive shaft of which is driven by the intermittent movement of the nipper crank arm via a drive train. drive shaft drive. The required clamping force and the required opening position of the nippers can be achieved by means of this device.

Due to the high number of combing cycles (for example 350 combing cycles/min), great accelerations and loads on the support occur when the nipper group is opened and closed. Therefore, especially when a higher number of combing cycles is to be achieved, it is required that the motion sequence of the upper nipper should also be adapted accordingly so that the acceleration forces can be kept to a minimum. However, the above-mentioned requirements can only be met with great effort and expenditure with the device described.

In a past patent application (DE-A 14216485) of the applicant, this requirement was proposed as a starting point to replace the previous mechanical drive of the eccentric shaft with an electric motor drive. With this device it is now possible to adjust or operate the upper nipper according to different motion profiles by correspondingly controlling the drive motor. In addition, with this device it is possible to compensate for "variation of the gap between the nipper and the detaching roller" of the nipper movement.

In order to ensure the synchronization between the drive motor and the movement of the nipper, a sensor is used to detect the rotation angle of the circular comb shaft and transmit the relevant signal to the controller of the motor.

With this device, various adjustment possibilities of the upper nipper movement required by actual work can be realized. However, such devices have proven to be relatively expensive and require accurate calibration in order to monitor the angle of rotation of the circular comb axis. Furthermore, the entire system depends on the functionality and lifetime of the monitoring sensors.

Contents of the invention

The object of the present invention is therefore to invent a device which contains the advantages of the DE'485 described, but which is cheap and provides a drive possibility which ensures the movement of the upper nipper and the lower jaw at any time. There is reliable synchronization of plate and circular comb movements.

The measure taken for this purpose is that at least one transmission stage with non-circular gears is assigned to the axis about which the elastic columns pivot, for displacing this axis.

An advantageous proposal is that the elastic columns are each pivotably supported on an eccentric wheel, which is driven by a drive shaft supported in the machine frame, wherein the drive shaft is fixedly mounted on the drive shaft in a rotationally fixed manner. At least one non-circular gear.

With the proposed arrangement of the gear train with non-circular gears, it is possible to implement an optimal curve of motion of the upper nipper according to the designed gear shape.

It is also conceivable to replace the drive train with non-circular gears by another pair of likewise non-circular gears in order to be able to re-adapt to the changed conditions when the material to be processed changes.

It is also proposed that the transmission stage with non-circular gears is connected to the drive shaft of the nipper set via a further transmission stage (for example with circular gears). This ensures that the movement of the upper nipper is synchronized with the movement of the remaining nipper group and also with the rotational movement of the circular comb, since the drive of the nipper shaft and the drive of the circular comb shaft are mechanically interconnected.

Another embodiment is also proposed, in which the gear stage with the non-circular gears is geared to the main gear drive driven by the main electric motor via a further gear stage. With this arrangement, unlike the previously described solution, the transmission stage can be driven with a continuous rotational speed.

It is also proposed that the non-circular input gear of a transmission stage and the output gear of another transmission stage be rotationally fixed on the same shaft.

In order to compensate for changes in the distance between the nippers and the separating rollers, it is proposed that at least one gear wheel of a further gear stage be connected to the associated drive shaft via a detachable connection.

As a result, changed nipper end positions can be adapted even during the movement of the upper nipper.

Description of drawings

Further illustrate other advantages of the present invention below by means of the embodiment that accompanying drawing shows: Drawing shows:

Fig. 1 is a schematic vertical section through a part of the combing head of a combing machine;

Figure 2 is a schematic diagram of the parts shown in Figure 1 in different positions;

Fig. 3 is a graph showing the variation of the opening degree of the combing head nipper group with the position of the nipper group;

Fig. 4 is a reduced and simplified diagram corresponding to Fig. 1 and has shown the additional driving parts of the nipper group;

Figure 5 has an enlarged view of the input gear of another transmission stage according to Figure 4 with a detachable connection; and

FIG. 6 is a side sectional view according to FIG. 5 .

Detailed ways

In Fig. 1, represented the combing head of its part in 2 and 4 to comprise a circular comb shaft 1 of continuous rotation, two detaching rollers 2 and 3, and a nipper shaft 4 of swingable rotation, they are all supported on Inside a machine rack not shown. The nipper shaft 4 supports the crank arm 5, and the rear end of the lower nipper frame 6 is hinged on the crank arm. The front end of lower nipper frame 6 is hinged on the front bearing 7, and the latter can be supported around circular comb shaft 1. The nipper 8 is installed on the lower nipper frame 6, and the upper nipper 9 works together with it. Last nipper 9 is contained on the upper nipper arm 10, and upper nipper arm is connected with lower nipper frame 6 and can turn around shaft 11. In addition, the upper nipper arms 10 are each articulated on an elastic column 12 which is pivotable about an axis A. Through the swinging rotation of the nipper shaft 4 , the lower nipper frame 6 is reciprocated between the front end position shown in FIG. 1 and the rear end position. In FIG. 2, the front end position is schematically indicated by a thick solid line, and the rear end position is schematically indicated by a thin line. In the rear end position the elastic post 12 holds the nipper group in the closed position, that is to say it presses the lower edge of the upper nipper 9 against the front edge of the lower nipper 8 via the upper nipper arm 10 . Thus between these two edges the fiber tufts are clamped from the lap to be carded (not shown), which is combed by a circular comb section 13 which is fixed to a comb mounted on the circular comb shaft 1. Round combing roll 14 (combroll).

In the front terminal position of the nipper group 6, 8, 9, 10, the elastic column 12 keeps the nipper group in an open state, that is to say, the elastic column 12 moves the upper nipper 9 away from the lower nipper 8 through the upper nipper arm 10 . The combed fiber bundles are separated from the laps left on the lower nipper 8 by detaching rolls 2, 3.

The cotton roll (feed roll) 15 (Fig. 1, Fig. 4) supported in the lower nipper frame is used to continue conveying a section of the lap to be combed when the nipper group is opened. The rotation of the cotton roller can be done in a conventional manner, when the nipper group 6, 8, 9, 10 is opened and/or closed, that is, during the forward movement of the lower nipper frame 6 and/or during the backward movement, through the upper The nipper arm 10 performs a rotary motion relative to the lower nipper frame 6 to generate. The rotary motion of upper nipper arm 10 is transmitted to cotton roller 15 by ratchet, freewheel or pattern plate (not shown among the figures), for example. A gear stage with non-circular gear wheels 16, 19 is assigned to the rotary axis A (FIG. 1) for moving this axis A. In this case the axis of rotation A is the axis of the eccentric 17 mounted on a shaft 18 mounted in the machine frame, on which the gear wheel 16 of the transmission stage 20 is also mounted in a rotationally fixed manner. The elastic column 12 is mounted pivotably on an eccentric 17 . On the input shaft 21 of the transmission stage 20 , a gear wheel 22 is mounted in a rotationally fixed manner, which meshes with a further gear wheel 24 . This transmission stage with gearwheels 22 and 24 represents another transmission stage. The teeth of the non-circular gears in meshing state are only partially and schematically shown in FIG. 1 .

FIG. 1 shows two drive possibilities for the input gear wheel 24 of the transmission stage 23 . The driving connecting line V represented by the dotted line represents that the input shaft 4a and the driving shaft 4 of the nipper group can overlap. That is to say that the drive gear 24 is coaxially fixed on the shaft 4 of the nipper group. Since the shaft 4 does not rotate a full revolution but performs an intermittent motion (forward and backward motion), it is possible to design the drive gear 24 with only partial tooth segments for transmitting intermittent motion to the drive gear twenty two.

A second drive possibility of the gear wheel 24 is shown in dashed lines, wherein the drive shaft 4 a is connected via a drive connection 29 to the main drive 26 , which is connected to the main motor 27 via a drive connection 30 . The advantage of this second solution is that it enables the drive gears 16, 19, 22 and 24 to perform a continuous rotational movement, which has a positive effect on reducing the wear of the gears as a result. In this continuous motion scheme, the position of the drive shaft 18 relative to the eccentric wheel 17 should be properly matched to obtain the desired ideal motion curve of the upper nipper 9 ( FIG. 3 ).

FIG. 4 shows, in a reduced view, a crank mechanism which causes the drive shaft 4 of the crank arm 5 of the nipper to reciprocate. The crank drive mainly consists of a crank disc 42 that rotates around a drive shaft 41 . A push rod 43 is rotatably articulated on the crank plate 42 via a crank pin 44 , which is inserted into a guide 45 which is connected to the shaft 4 in a rotationally fixed manner.

In order to adapt this system to process different fiber lengths (fiber average length), it is necessary to change accordingly when the nipper group is at the frontmost position, between the clamping points of the separating rollers 2, 3 and the feeding roller and the lower nipper 8. The distance between the gripping points. This distance is called the distance between the nipper and the separation roller (separation distance). This distance also determines the most forward position of the lower nipper 8 relative to the clamping point of the detaching rollers 2 and 3 . This distance is represented schematically by E and E1. Changing the distance from E to E1 is achieved by releasing the guide 45 and rotating it relative to the nipper shaft 4 by an angle α. After this rotation, the rotationally fixed connection between the shaft 4 and the guide 45 is re-established. This adjustment also changes the movement of the upper nipper 9 , which is influenced by the movement of the lower nipper. In order to now re-establish the original kinematic relationship between the lower nipper 8 and the upper nipper 9, it is proposed (FIG. 5) to rotate the drive gear 24 relative to the drive shaft 4a. As can also be seen in particular from FIG. 6 , a ring 33 is mounted on the shaft 4 a in a rotationally fixed manner. Ring 33 is formed with flange 34 and carries gear 24 . The gear wheel 24 is formed with three slots 36 into which a screw 35 is inserted, which is screwed into a threaded hole 40 in the flange 34 of the ring 33 . That is to say, the gear wheel 24 is rotationally fixedly connected to the ring 33 and thus to the shaft 4 a by means of a screw 35 . Now to compensate the angle α set by the guide 45 , the screw 35 is loosened and the adjustment is carried out according to the predetermined scale 48 . This adjustment is selected according to a predetermined table in which the adjustment to be carried out by means of the scale 48 is indicated by means of the adjustment angle α. The setting angle α is indicated as an example only, and the adjustment of the guide 45 can also generally be carried out by means of a scale similar to that indicated, for example, at 48 .

The idea of compensating for variations in the gap between the nipper and the detaching rollers by rotating the drive gear relative to the shaft on which it is supported to rotate its angular position can also be applied to designs that do not use non-circular gears.

Due to the described construction, an economical and reliable arrangement is obtained for the movement process of the upper nipper 8 .

Claims (6)

1. The combing machine has a swinging nipper set (6, 8, 9, 10) connected to the driving device. This nipper set includes a lower nipper frame (6) and an upper nipper swingably connected thereto Plate arms (10), the latter are respectively hinged on an elastic column (12) that can swing around the shaft (A), and are characterized in that: the shaft (A) is equipped with at least one non-circular gear (16, 19) The transmission stage (20) is used to move the shaft (A). 2. According to the described combing machine of claim 1, it is characterized in that: the elastic columns (12) are respectively swayably supported on an eccentric wheel (17), and the eccentric wheel passes through a drive shaft (18) supported in the frame. ) drive, at least a non-circular gear (16) of a transmission stage (20) is fixedly mounted on this drive shaft (18). 3. According to the described combing machine of one of claims 1 to 2, it is characterized in that: the transmission stage (20) passes through another transmission stage (23) and the drive shaft of the nipper group (6, 8, 9, 10) (4) Connection. 4. The combing machine according to one of claims 1 to 2, characterized in that: the transmission stage (20) is connected in transmission with the main transmission (26) by another transmission stage, and the latter is driven by the main motor ( 27) Drive. 5. Combing according to one of claims 3 or 4, characterized in that the non-circular input gear (19) of the transmission stage (20) and the output gear (22) of the other transmission stage (23) are fixed in rotation Ground is contained on the same axle (21). 6. According to the described combing machine of one of claims 3 to 5, it is characterized in that: at least one gear (22, 24) of another transmission stage (23) is connected to the relevant drive by a detachable connection (35) Shafts (4a, 21) are connected.

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