JPH0157033B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a yarn winding device, and in particular to a yarn winding device that traverses and creeps the yarn supplied at a constant speed from side to side using a traverse guide. This invention relates to a device for winding yarn onto a package which is pressed against a friction roller and driven to rotate.

[Background of the invention]

In false twisters, take-up machines, etc., yarns fed continuously at a constant speed are generally wound into cheese packages. The package is driven in pressure contact with the surface of a friction roller that rotates at high speed, and the traverse of the yarn is performed by the reciprocating motion of a traverse guide that is linked via a shaft with the rotational motion of a traverse drum in a cam box. .

In the above-described yarn winding method, the traverse guide is usually caused to perform a movement called creeping in order to prevent so-called selvedge height.

As shown in Fig. 1, this creeping effect to prevent the height of the ears is caused by the time T during which the traverse guide is moving at the maximum traverse width and the time T during which the traverse guide is moving at a width smaller than the maximum traverse width. In other words, it is known that it increases or decreases in correlation to the creeping time t.

That is, the creeping ratio (α=t/T+t
×100) is closer to 100%, the occurrence of ear height in the package decreases, and it is known that the ear height itself becomes lower.

However, when the creeping ratio α is increased in order to prevent selvage height, twill drop tends to occur, and twill drop tends to occur particularly at the beginning of winding a package with high thread tension.

[Purpose of the invention]

Therefore, this invention is based on the above knowledge, and the optimum creeping ratio is given to each individual package in a false twisting machine, spinning winding machine, etc. according to the winding thickening process, and as a result, the selvage height is reduced. To provide a novel yarn winding device capable of obtaining a package that is free from formation and twill drop.

〔Example〕

Hereinafter, embodiments will be described based on the drawings.

In Figure 2 and below, 1 is the cradle arm 2.
The package cage is supported at both ends by the friction roller 3 and is pressed against the friction roller 3.

Reference numeral 4 denotes a traverse guide sandwiched between a traverse drum 6 having a traversing groove 5 on its outer periphery and a cam plate 8 having a groove 7 on its inner surface in the longitudinal direction. 4 is formed in an L-shape, and the shaft 10 of the bent portion is engaged with the traversing groove 5, and the shaft 12 provided on one arm 11 is engaged with the groove 7, so that the traverse width is the same as that of the cam plate. It is designed to be increased or decreased by the swinging of 8.

That is, when the cam plate 8 is rotated in the direction of arrow A in FIG. The reciprocating width becomes larger as it turns in the direction.
Note that the pivot center 15 of the cam plate 8 is aligned with the center of the cam plate 8. Reference numeral 16 denotes a spring that constantly biases the cam plate 8 in the opposite direction of arrow A.

Next, the traverse width changing device 13 will be explained.

17 is a substantially Y-shaped arm rotatably supported around a shaft 18 provided on a machine frame (not shown);
At the end of one arm 20 of the Y-shaped arm 17, there is further a letter-shaped arm 23 having two arms 21 and 22.
is rotatably mounted on a shaft 24, and a rod 14 for pulling the cam plate 8 is connected 25 to the end of one arm 21 of this dogleg-shaped arm 23.

Cam rollers 28 and 29 are attached to the ends of the other two arms 26 and 27 of the Y-shaped arm 17, respectively. An eccentric cam 30 is provided which is rotated slowly according to a program, and a plate-shaped cam 32 is provided on the cradle arm 2 via a bracket 31 in relation to the cam roller 29. A cam roller 33 is also attached to the other arm 22 of the dogleg-shaped arm 23.
It is designed to engage with a three-circular cam 34.
Reference numeral 35 is a spring stretched between a shaft provided on the machine frame (not shown) and a shaft on the Y-shaped arm 17, and urges the Y-shaped arm 17 in the clockwise direction in FIG.

Next, the operation of this embodiment device will be explained with reference to FIGS. 4 and 5.

As mentioned above, the reciprocating width of the traverse guide 4, that is, the traverse width, decreases when the cam plate 8 is operated by the traverse width changing device 13 in the direction in which the cam plate 8 turns to the left (arrow A), that is, in the direction in which the rod 14 is pulled. It increases when the rod 14 is operated in the opposite direction, that is, in the direction in which the rod 14 is returned, so that at the beginning of winding the package 1 (FIG. 4A), the cam roller 33 is at the base end of the 1/3 circular cam 34. abutting the side,
Since the doglegged arm 23 has rotated to the right around the shaft 24 and the rod 14 has been returned, the traverse width is at its maximum (Fig. 4A), and the package 1 has become thicker and is in the cradle. When the arm 2 pivots upward and the cam roller 33 comes into contact with the tip side of the 1/3 circular cam 34, the doglegged arm 23 gradually pivots to the left around the shaft 24 and the rod 14 is pulled (Fig. 4). C) The traverse width gradually decreases.

The trajectory of the gradual decrease in the traverse width caused by the cam 34 and the cam roller 33 appears as an inclination of two parallel chain lines M in the diagram of FIG. 5 showing changes in the traverse width over time. There is a taper .theta. (FIG. 6) on both sides of .The operation of the eccentric cam 30 and the cam roller 28 in addition to the gradual reduction of the traverse width to form this taper will be explained next.

That is, the doglegged arm 23 rotates gently to the right around the shaft 24 throughout the entire winding process as the package cage 1 becomes thicker as described above.
During this time, the doglegged arm 23 is swung left and right about its fulcrum 24 in short cycles by the rotation of the eccentric cam 30, and the rod 14 is also reciprocated in short cycles, resulting in a short traverse width. A creeping operation is performed within a width l corresponding to the amount of eccentricity of the eccentric cam 30 at regular intervals.

The trajectory of the creeping operation is represented by a zigzag line N between the two parallel chain lines M in FIG.

Then, the folded straight line portion Na on the left side of FIG. 5 of the zigzag line N representing the above creeping operation
represents a maximum width traverse motion similar to T representing the full width traverse state in FIG. The creeping ratio can be changed to any desired ratio by changing the program, but in this embodiment, the creeping ratio is changed to the eccentric cam 30.
Without changing the movement program of the package 1, the winding is made small for each package depending on the diameter of the package 1, gradually increasing at the beginning of winding, and increasing to a constant value afterward.

That is, in the device of this embodiment, at the beginning of winding the package 1, the plate-shaped cam 32 attached to the cradle arm 2 contacts the cam roller 29 of the Y-shaped arm 17 (FIG. 4A), and the eccentric cam 30 causes the The rightward rotation of the letter-shaped arm 17, that is, the rotation in the direction of increasing the traverse width, is prevented at a certain position.
The actual amount of eccentricity caused by this is reduced to Δl.

Therefore, within the angular range in which rightward rotation is prevented by the plate-shaped cam 32, the Y-shaped arm 17 is not affected by the eccentric cam 30 and does not rotate for a certain period of time (FIG. 4A). . In other words, although the eccentric cam 30 moves at a constant cycle according to a predetermined program, the Y-shaped arm 17 moves at the maximum width traverse portion (the maximum width traverse section) at the constant cycle at the beginning of winding the package 1. The Na part indicated by the dotted line in Figure 5) is
The traverse guide 4 is caused to traverse along a trajectory corresponding to the zigzag line N shown as a solid line in FIG. The creeping rate (α=Nb′/Na′+Nb′×100) is Na<
Since Na', Nb>Nb', it is substantially made small.

Moreover, the amount of creeping is also reduced to Δl.

Thereafter, the package 1 becomes thicker, and the plate-shaped cam 32 moves toward the cam roller 2 as the cradle arm 2 rotates.
If you move to a position away from 9 (Fig. 4 B, C),
As described above, the Y-shaped arm 17 and the doglegged arm 23 achieve the eccentricity l by only the interaction between the cam roller 28 and the eccentric cam 30, and the cam roller 33 and the 1/3 circular cam 34, respectively. A large creeping rate (α=
The thread is wound with Nb/Na+Nb×100).

As is clear from the above description of the embodiment device, according to the yarn winding device of the present invention, the creeping rate at the beginning of winding onto a package is substantially small, and thereafter, as the package becomes thicker. Therefore, the creeping rate gradually increases, and later it can be maintained at a constant increased value, so as mentioned at the beginning, it is possible to create a high-quality package cage that does not cause selvage height or twill drop in the package cage that has been rolled up. Obtainable.

In addition, by simply replacing the plate-shaped cam 32, the rate of change in the creeping rate can be changed to an arbitrary degree, and the length of the section where the creeping rate gradually increases (that is, the section where the creeping rate is small) can be easily changed. Since it can be changed, it can be adjusted according to the size of the winding diameter of the package.
Another advantage is that the creeping rate can be set to a small value only in the winding start section where twill drop is particularly likely to occur.

Furthermore, in the above-described embodiment, the creeping rate is controlled based on the tilt angle of the cradle arm, which is a displacement amount specific to each package, which is different from the eccentric cam 30. There is no need to perform complicated control such as changing the movement program of the eccentric cam 30 for each package depending on the amount of winding. ,
This invention has the great advantage of being extremely easy to implement in a winding device in which the creeping movement of a large number of package winding devices is performed by a large number of eccentric cams fitted onto a single shaft.

[Brief explanation of drawings]

FIG. 1 is a diagram representing the normal traverse and creeping motion of the traverse guide;
FIG. 2 is a side view of the yarn winding device according to the present invention;
Fig. 3 is a view from Fig. 2 of the traverse device with the cover removed, Fig. 4 is an explanatory diagram of the action;
Figure 5 is a diagram showing the traverse and creeping motion when the yarn is wound using the yarn winding device shown in Figures 2 and 3, and Figure 6 is a schematic diagram showing the package being wound up. be. 1...package, 2...cradle arm, 4...
Traverse guide, 5... Traverse groove, 6... Traverse drum, 7... Guide groove, 8... Cam plate, 14... Rod, 17... Arm, 30... Eccentric cam, 32... Plate cam.

Claims (1)

[Claims] 1 A traverse guide is provided between a traverse drum provided with a traversing groove and a cam plate provided with a guide groove in the longitudinal direction, and the traverse guide is traversed from side to side by the rotation of the traverse drum, and the traverse guide is traversed from side to side by the rotation of the traverse drum. Therefore, the device is a device for winding a thread around a rotating package while increasing or decreasing the traverse width of a traverse guide, and an eccentric cam for swinging the cam plate is provided to engage one end of the arm interlockingly connected to the cam plate. A yarn winding device characterized in that a plate-shaped cam is provided on the cradle arm and protrudes from the cradle arm, the plate-like cam being engaged with the other end of the arm and regulating the swinging limit of the arm.