JPS5947731B2 - Method and device for correcting intra-lap weight fluctuations in a lap machine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a sliver wrapping machine for forming a sliver produced by a card or a filament machine into a wrap, or to a ribbon wrapping machine for polymerizing the wrap produced by a sliver lapping machine.

As shown in FIG. 10, the conventional sliver lapping machine takes out the sliver S from a plurality of cans 1, and moves the fixed guide 2, lifter roller 3a,
3b1 press roller 4a.

4bt draft roller 5a, 5bt62>6bt calendar roller? a t 7 b ) 8 a , 8
A pressure rack 10 is placed on the winding rollers 9a and 9b via b.
The wrap L is wound into the shape of a package P on a wrap spool 11 which is held under pressure.

Note that a pinion 12 is engaged in order to apply pressure to the pressurizing rack 10.

In the conventional device configured in this way, the rotational speed of each roller 3, 4, 5, 6, 7, 8, 9 during winding is set to a fixed constant value, and the winding is carried out on the wrap spool 11. The variation in the amount of lap L caused by this was limited as much as possible.

However, as the wrap L wound around the Lovesfure 11 approaches the end of the winding from the start of winding, that is, as the diameter of the package P becomes larger, the winding roller 9
It becomes difficult for the driving force to be transmitted from a, 9b to the package P, and tension fluctuations occur between the calender roller 8 and the take-up roller 9a.

As a result, the weight of the wrap L taken up on the wrap spool 11 showed a tendency to gradually increase in weight as shown in the center of FIG. 9, and even when actually measured under relatively good operating conditions,
It was found that the change in wrap weight occurred by around +5%.

It should be noted that the larger the package size, the larger the change in the amount of wrap, which is a major obstacle to promoting large packaging.

Further, if there is a change in the weight of the wrap, that change will eventually lead to a change in the yarn count, which has a great effect on the product and significantly reduces the product value.

Therefore, it is necessary to reduce the fluctuation in the lap weight in the next process, for example, in a combing machine, and conventionally, the influence of the fluctuation in the luff weight has been reduced by setting up the wrap.

For example, if the combing machine doubles 4 wraps, it will take 2 steps (supplying 2 full wraps and 2 half wraps) or 4 steps (1 full wrap, 1 + lap, 1 + lap, 1 + lap each).
book supply).

Of course, if the number of setups is increased, the weight fluctuation of the spun intermediate product (lap or sliver) will be greatly reduced. This has disadvantages in that production efficiency decreases and the amount of work for setup workers increases significantly.

The present invention aims to eliminate such conventional drawbacks and provide a method and apparatus for forming a package without any variation in the amount of wrap even if it is made into a large package.

The gist of the invention is to take out a plurality of wraps or slivers;
In a wrapping machine, a wrap is passed between a series of rollers and wound onto a wrap spool held under pressure by a pressure rack on a take-up roller.A draft is applied to any section of each of the rollers, and the wrap is wound onto the wrap spool. As the winding diameter of the wrapped wrap increases, the draft amount is gradually increased to make the internal weight of the wrap uniform.

In other words, as shown in A in Fig. 9, it has been found that the fluctuations in the weight of the wrap do not occur irregularly, but rather gradually and regularly. As the diameter increases, the draft is gradually increased within the wrap passing roller group as the wrap diameter increases.

An actual case of the present invention will be described below with reference to FIGS. 1-A and 1-B.

Fig. 1-A shows a conventional sliver lapping machine equipped with a correction device for achieving the method of the present invention, and the same numbers and symbols as in Fig. 10, which are shown as the conventional device, represent the same members. Therefore, the explanation will be omitted and only the main parts of the present invention will be explained.

This is V, P, S, (Variable PitchS
This is a first embodiment using a calender roller 8b, which is configured to input power from a calender roller 8b to increase the speed of the take-up roller 9a. , sprocket 32, electromagnetic clutch MC5, sprocket 33, chain 34, and sprocket 35 to input shafts 36 for v, p, and s.

On the other hand, from the output shaft 37 of v, p, s, a sprocket 38,
Chain 39, sprocket 401 electromagnetic clutch MC6
, sprocket 41, chain 42, sprocket 43
The speed-changed rotation is transmitted to the winding row 9a via the winding row 9a.

Also, M3 is ■. This motor is for adjusting the P and S speed ratios, and rotates the V, P, and S speed change shafts 47 via a sprocket 44, a chain 45, and a sprocket 46.

The motor M3 is rotated by a rotation control device 48 according to a predetermined program within this control device.

Of course, the rotation may be controlled in conjunction with the bank meter.

Also, M4 rotates in the opposite direction to motor M3, and after the tube is full, ■.

This is a return motor for returning the P and S gear ratios, and is connected to a sprocket 51 via a sprocket 49 and a chain 50.

More M. When restoring the gear ratio of v, p, s, v,
This is a motor that drives p and s, and sprocket 5
2. Input shaft 3 via chain 53 and sprocket 54
It is connected to 6.

(Because the gear ratio of v, p, and s cannot be changed unless they are rotating) Motor M3.

M4 and M5 have built-in electromagnetic clutches (not shown) so that they can rotate freely when not in operation.

To return the gear ratios of v, p, and s to their original states after the pipe is full, set the electromagnetic clutches MC52MC6 to "disconnected" and turn off the motor M.
The motor M4 may be rotated while the motor M4 is being rotated.

With this structure, as the pressure rank 10 increases, the gear ratios of V, P, and S are set steplessly higher, and a draft gradually becomes larger between the calender roller 8 and the take-up roller 9a. will be granted.

In other words, despite the tendency for the diameter of the package P to become larger and the wrap weight to become heavier, the draft amount increases as shown in A in Figure 1-B, so the wrap weight becomes heavier as shown in Figure 9. As shown in B, it can always be kept constant.

Furthermore, in this embodiment, if the motor M3 is capable of forward and reverse rotation, the motor M4 can be omitted and the motor M3 can be rotated forward and backward.
The gear ratio can be set in stages by the control method of 3.

(Refer to the middle part of Fig. 1-B) Next, a second actual case using a ring cone shifting mechanism will be explained with reference to Figs. 2-A and 2-B.

In the figure, M1 is a main motor for driving each roller. Power is transmitted from the sprocket 13 to the sprocket 14 via the chain 15 to drive the take-up roller 9a, and the rotation of the take-up roller 9a is input to the ring. The output of the ring cone transmission R is transmitted to the calendar jig 8b.

Note that the take-up roller 9b is rotated synchronously in the same direction from the take-up roller 9a through an intermediate gear (not shown), and from the calendar roller 8b through a gear train (not shown), each roller 7 It will be rotated by .6,5°4.3.

Reference numeral 16 denotes a speed change sprocket for setting the speed ratio of the ring cone transmission R, and is connected to the sprocket 12a of the re-pinion 12 via a chain 17.

With this configuration, as the pressurization rank 10 increases, the gear ratio of the ring cone transmission FIR is set steplessly higher, and as the diameter of the package P increases, the draft amount increases as shown in Figure 2-B. Since the amount increases as shown in FIG. 9, the amount of lap can always be kept constant as shown in FIG. 9B.

Next, a third example of leprosy will be explained with reference to FIGS. 3-A and 3-B.

This third practical example uses a transmission using a differential gear mechanism, and the main motor M is connected to the differential gear mechanism in the figure.
The rotation of the take-up roller 9a driven by the sub-motor M2 is transmitted as the first input, and the rotation of the sub-motor M2 is transmitted as the second input via the sprocket 18, the chain 19, and the sprocket 20.

Furthermore, the output from the differential gear mechanism is the calendar roller 8b.
Similarly to the first actual case, each roller 7.6,
5, 4, and 3 will also be rotated synchronously.

Further, the rotation speed of the sub-motor M2 is controlled by each limit switch LS1. By sequentially operating the LS3, the rotational speed is controlled to be switched via the control device 26.

In the case of this third example, the gear shift is carried out in stages as shown in Figure 3-B, and the lap amount control is approximated as shown in Figure 9-B.
It was designed so that

Next, a fourth embodiment will be described with reference to FIGS. 4-A and 4-B.

The fourth example is similar to the third example in that a differential gear mechanism is used, but it is a simplified version of the third example.

That is, the rotation of the take-up roller 9a is taken as the first input, and the rotation of the take-up roller 9a is taken as the second input, and the electromagnetic clutch MC6 and the gear train G1. G2. The rotation of the take-up roller 9a is controlled via G3.

Furthermore, gear train G1. G2. An electromagnetic brake 23 is provided on the G3 side.

Then, the electromagnetic clutch MC6 is released and the electromagnetic brake 23 is released.
The timing of the operation is determined by the limit switch LS4 operated by the dock 10a.

With this configuration, the limit switch LS
4 is activated, the first input and the second input are input to the differential gear mechanism, and the limit switch LS4 is set to O.
After NL, only the first human power is applied to the differential gear mechanism, and the rotation speed of the calender roller 8b is changed.

This fourth practical example is effective in reducing the amount fluctuation after the winding amount increases and setting the overall lap amount fluctuation low, and is simple in structure and economically effective.

Next, regarding FIG. 5, the fifth example using a slip control clutch
An actual case will be explained.

In the figure, MC7 is a slip control clutch, which is disposed between the take-up roller shaft 21 and gear trains G4 and G5 t06.
The number of rotations of the calender roller 8b is changed by changing the slip rate.

That is, when the package diameter increases and the pressurizing rack 10 rises and the limit switches LS, LS7 are sequentially activated, the resistance within the control device 25 is sequentially loaded, reducing the eddy current generated in the slip control clutch MC7. , the number of rotations of the calender roller 8b is changed by increasing the slip ratio.

(The gear ratio becomes stepwise as shown in the middle of Figure 1-B shown in the first actual winding example.) As a method of changing the slip rate of the slip control clutch MC7, it is possible to change the slip ratio according to the rotation speed of the pinion 12. It is also possible to load the resistance steplessly.

(The gear ratio is stepless as indicated by A in Figure 1-B.) Next, Figures 6-A and 6-B will be explained using a sixth actual case of a transmission means that combines a gear train and an electromagnetic clutch. do.

In the figure, 29 is an input shaft, 25 is an output shaft, G7 is a gear fixed to the input shaft 29, G8 is a gear fixed to the input shaft 29 by the operation of the electromagnetic clutch MC1, and 26 is the first intermediate shaft. A gear G9 that meshes with the gear G8 is fixed, and a gear G1o that meshes with the gear G8 and is fixed to the first intermediate shaft 26 by the operation of the electromagnetic clutch MC2 is attached. .

Reference numeral 21 denotes a second intermediate shaft, and a gear G1□ that meshes with the gear G8 is fixed to the shaft 27.

Further, a gear G12 is fixed to the output shaft 25, and a gear G1 is attached to the second intermediate shaft 2γ.
A gear G13 that meshes with the gear G1 and is fixed by the operation of the electromagnetic clutch MC3 is attached.

Furthermore, a gear G14 is fixed to the third intermediate shaft 28, which meshes with the gear G1□ of the output shaft 25, meshes with the gear G13, and is activated by the operation of the electromagnetic clutch MC4. A fixed gear G□5 is attached.

In the sixth embodiment configured in this way, each gear G7
By changing the number of teeth of G14 and the operation timing of each electromagnetic clutch MC1 to MC4, the rotation of the input shaft 29 can be changed in speed and transmitted to the output shaft 25.

For example, the number of teeth of gear G7 is 66, the number of teeth of gear G8 is 43,
Gear G9 is 62, gear G1o is 41, gear G11 is 41
, gear G12 is 64, gear G13 is 43, gear G14 is 9, gear G15 is 45, and each electromagnetic clutch MC1~
By switching the operating timing of the MC, four-speed shifting is possible.

That is, (1) By operating the electromagnetic clutches MC1 and MC3, the rotation ratio of the output shaft 3 to the input shaft becomes i=1, and the input shaft and the output shaft rotate synchronously.

■Also electromagnetic clutch MC22MC5, 66X41 If you operate, the rotation ratio will be.

. It becomes X43 L 015. ■Electromagnetic clutch MC1
, If MC4 is activated, the rotation ratio is 43x69-i, 03
It becomes 0.

■Electromagnetic clutch 45X64-,,,,66X
If you operate 41 x 69MC22MC4, the rotation ratio will be 6
2 x 45 x 64 = 1.046.

In this way, the rotation ratio of ■ to ■ will be obtained, so the input shaft is connected to the calendar roller 8b, the output shaft is connected to the take-up roller 9a, and the calendar roller 8b is driven by the main motor. With this configuration, it is possible to increase the speed of the take-up roller 9a and provide a draft between the calender roller 8 and the take-up roller 9a.

In addition, to set the operation switching timing of each electromagnetic clutch MC1 to MC4, a limit switch may be used as in the third to fifth actual cases, or the switching operation may be performed in accordance with the winding amount in conjunction with a bank meter. You can do it like this.

Next, a seventh embodiment in which a pulse motor is used to drive the take-up roller 9b will be described with reference to FIGS. 7-A and 7-B.

In the figure, PE is a pulse encoder connected to the main motor M1, which generates a predetermined number of pulses according to the rotation speed of the main motor M1, and is configured to rotate the pulse motor PM via a speed command device 55 and a control device 56. has been done.

GBl and GB2 are gear boxes, and pulse motor P
M connects winding rollers 9a and 9 via gear box GB2.
Rotate b.

Note that the speed command device 55 increases the number of pulses from the pulse encoder PE at a constant rate and inputs a signal to the control device, so the pulse motor rotates at a constant rate higher than the rotation speed of the main motor M1. will be done.

Next, an eighth actual case will be described with reference to FIG. 8, in which the amount of sliver supplied was gradually decreased as the winding diameter increased to make the amount of wrap uniform.

In the figure, reference numeral 57 denotes a drive shaft that is connected to one drive source (not shown) and rotates at a constant rate, and drive taper cones 58 are fixed thereto in correspondence with the number of slivers S.

Reference numeral 59 denotes a driven taper cone that grips the sliver S in contact with the driving taper cone 58, and is rotatably supported.

Reference numeral 60 denotes a sliver guide bar to which a sliver guide 61 is fixed, and is configured to be moved via a chain 62 in response to rotation of the pinion 12.

Therefore, as the rack 10 rises, the sliver guide bar 66 moves in the X direction, moving the sliver S to the smaller diameter side of the drive taper cone 58, reducing the amount of sliver S supplied and correcting the variation in the amount of wrap. It is something.

Note that in the actual winding example above, the draft amount is mainly changed between the take-up roller and the calender roller, but since the variation in the amount of weight within the wrap changes almost regularly and can be predicted, It may be done in between.

As described above, the present invention uses a wrapping machine that takes out a plurality of wraps or slivers, passes them between a series of rollers as wraps, and winds them onto a lap spool held under pressure on a take-up roller. By gradually increasing the draft amount as the winding diameter of the wrap applied and wound on the wrap spool increases, the change in weight between the start of winding and the end of winding of the rewrap is suppressed, It is possible to wind up a uniform amount of wrap, making it possible to create large packages.

Furthermore, setup work in the next process can be made unnecessary, resulting in the effect of significantly improving product quality and productivity.

[Brief explanation of the drawing]

The figures show an actual sister example of the present invention, FIG. 1-A is a main drive system diagram showing the first practical example, FIG. 1-B is a transmission diagram thereof, and
Figure A is a main drive system diagram showing the second embodiment, Figure 2-B is a transmission diagram thereof, Figure 3 is a diagram of the main drive system showing the third embodiment, and Figure 3-B is a transmission diagram thereof. , Fig. 4 is a main part drive system diagram showing the fourth embodiment, Fig. 4-B is a transmission diagram thereof, Fig. 5 is a main part drive system diagram showing the fifth actual case, and Fig. 6 is a main part drive system diagram showing the fifth example. The main part drive system diagram showing the case, Fig. 6-B is the transmission diagram, Fig. 7 is the main part 1 drive system diagram showing the seventh actual case, Fig. 7-B is the transmission diagram, Fig. 8 is the transmission diagram. Main drive system diagram showing the 8th actual case,
Fig. 9 is an explanatory diagram showing the characteristics of the lap quantity, and Fig. 10 is an overall system diagram of the conventional device.
4... Press roller, 5, 6... Draft roller, 7, 8... Calendar roller, 9...
...Take-up roller, 10...Pressure rack, 11...Wrap spool, 12...
Pinion, R...Ring cone transmission, D...
...Differential garden wheel mechanism, 24...Slip control clutch, Ml...Main motor, M2...
...Sub motor.

Claims (1)

[Claims] 1. In a wrapping machine that takes out a plurality of wraps or slivers and winds them as wraps between a series of rollers onto a wrap spool held under pressure on a take-up roller, drafting is performed at any section of each of the rollers. A method for correcting intra-wrap weight fluctuations in a wrap machine, characterized in that the amount of draft is gradually increased as the winding diameter of the wrap wound on the wrap spool increases. 2. In a wrapping machine that takes out a plurality of wraps or slivers as wraps and winds them onto a wrap spool that is held under pressure on a winding roller through a series of rollers, the winding diameter of each of the rollers increases in conjunction with an increase in the winding diameter of the wrap spool. 1. A correction device for intra-wrap weight fluctuation in a lap machine, characterized by intervening a speed change means for changing the surface speed ratio in an arbitrary section.