JPH0350123Y2 - - Google Patents

Description

[Detailed description of the invention] Industrial application field This invention is a yarn winding machine, in particular, a yarn winding machine that uses a traverse guide to traverse the yarn fed at a constant speed from side to side and break the selvage, and then transfer the yarn to a friction roller. The present invention relates to a selvage breaking device for a winder that winds up a package that is pressed into contact with the package and is driven to rotate.

BACKGROUND OF THE INVENTION In temporary machines, take-up machines, etc., yarn that is continuously fed at a constant speed is generally wound into a cheese package. The package is driven in pressure contact with the surface of a friction roller rotating at high speed, and traverse of the yarn is performed by reciprocating motion against a traverse guide. In winding such yarn, the traverse guide is usually caused to perform a motion called selvage breaking in order to spin the yarn at a selvage height.

The relationship α=t/T+t×100 between the time t during which the selvage is performed and the time T during which the traverse guide moves with the maximum traverse width is called the selvage ratio. Although the occurrence of selvedge height is reduced in , as α is increased, twill drop tends to occur on one side, so it is necessary to set α appropriately. So, while making a cheese roll with the thread,
There is a need for a device that can provide the optimum selvage ratio depending on the yarn winding and thickening process.

Prior Art FIG. 6 shows a conventional device having the above-mentioned functions. (The method of winding the thread around the core axis using a traverse guide is a well-known and commonly used method, so a detailed explanation thereof will be omitted.) In the figure, 1 is supported at both ends by cradle arms 2; A package is pressed against a friction roller 3, 4 is a traverse guide, 6 is a traverse drum having a traversing groove on its outer periphery,
The traverse width is changed by changing the inclination of a cam plate (not shown) via a rod 14 by a traverse width changing device T as the package thickens.

To explain the traverse width changing device T,
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 square-shaped arm 2 having two arms 21 and 22.
3 is rotatably attached to the shaft, and the rod 14 for tensioning the cam plate is connected to the end of one arm 21 of the dogleg-shaped arm 23 at 25.

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, and this cam roller 33 engages a 1/3 circular cam 34 that is also attached to the cradle arm 2 via a bracket 31. It's starting to match. A spring 35 is tensioned between a shaft provided on the machine frame (not shown) and a shaft on the Y-shaped arm 17, and biases the Y-shaped arm 17 clockwise in FIG. ing.

Next, the operation of this conventional device will be explained.
As mentioned above, the reciprocating width of the traverse guide 4, that is, the traverse width, decreases when the rod 14 is pulled in the direction of arrow A in FIG. 6 by the traverse width changing device T, and increases when it is returned. .

FIG. 7 is an explanatory diagram of the operating state, and FIG.
indicates the state at the beginning of winding, the cam roller 33 is in contact with the base end side of the 1/3 circular cam 34, the dogleg-shaped arm 23 is rotated to the right around the shaft 24, and the rod 14 is in the position indicated by the arrow. The traverse width is now at its maximum. When the package 1 becomes thicker and the cradle arm 2 rotates upward in the counterclockwise direction, and the cam roller 33 comes into contact with the tip side of the 1/3 circular cam 34, the dogleg-shaped arm 23
gradually turns to the left around axis 24, and rod 14
is stretched as shown by the arrow in FIG. 7B, and the traverse width gradually decreases. This state of gradual decrease in the traverse width appears as the slope of the two two-dot chain lines M in FIG. (Since both the device of this invention and the conventional device shown in FIG. 6 have the same winding results, the second
Diagram available. ) Next, due to the rotation of the eccentric cam 30 and the cam roller 28, the dogleg-shaped arm 23 has its fulcrum 24 swinging from side to side in a short cycle, and therefore the rod 14 also swings in the eccentric cam in a short cycle. According to the amount of eccentricity of 30, the selvedge movement is performed within the width l. The locus of the mimiboshi motion is represented by a zigzag line N between the two parallel chain lines M and M in FIG. 2a. Figure 2b is an enlarged view, where the straight line part N _F on the left side of the zigzag line is the part where the maximum width traverse motion is occurring, and the valley part N _C is the part where the ear breaking motion is occurring. It is. this
Although the ratio of the N _F portion to the N _C portion may change the movement program of the eccentric cam, this conventional device does not change the movement program of the eccentric cam 30.
The selvage ratio is set small at the beginning of winding, gradually increased as the winding becomes thicker, and after a predetermined time, it becomes a constant value that increases.

That is, in the device shown in FIGS. 6 and 7, at the beginning of winding the package 1, the plate-like cam 32 attached to the cradle arm 2 moves toward the Y-shaped arm 1.
7 (FIG. 7A), and prevents the eccentric cam 30 from turning the Y-shaped arm 17 to the right, that is, from turning in the direction of increasing the traverse width, at a certain position. At the beginning of winding, the cam 30 reduces the actual amount of eccentricity to Δl. (Fig. 2) Therefore, within the angle range (A, B in Fig. 7) in which rightward turning is prevented by the plate cam 32, y
The eccentricity of the letter-shaped arm 17 is smaller than 1 regardless of the effect of the eccentric cam 30. package 1
is the position where the plate-like cam 32 is removed from the cam roller 29 as the cradle arm 2 rotates (7th position).
If the Y-shaped arm 17 and the dogleg-shaped arm 23 are moved to the cam roller 28, the eccentric cam 30, the cam roller 33, and the 1/3 circular cam 34, Only by their respective interactions, the yarn is wound with a selvedge breaking amount of eccentricity l and with a selvedge breaking ratio according to the movement program of the eccentric cam 30, as described above.

Problems to be Solved Conventional ear breaking devices have extremely complicated mechanisms, are difficult to manufacture and assemble, and have high production costs. It is necessary to realize this with a simple device.

Means for solving the problems In this invention, in order to solve the above problems,
A selvedge link is rotatably supported on a cam plate, and this link is connected at one end to a cradle arm via a feedback arm, while a cam plate is rotatably supported on a fixed fulcrum on the traverse guide. The strip link is connected to the feedback arm via another link, and the cam surface of the selvage ring is rotatably supported by the selvage bar, and is pulled toward the cam surface by a tension spring. The ear breaking device is configured to engage with a pulled ear breaking cam.

Function As shown in Figure 2a, when the yarn is wound around the winding shaft 11 while being traversed from side to side, as the winding becomes thicker, the cam surface for traversing is tilted and the traverse width is gradually reduced. Teyuki,
Its slope is shown by line M. Furthermore, the traverse width is determined by a mechanism such as a selvage bar, which is used to break the selvage between the lines MM' by a width l, as shown by the line N.
Furthermore, due to the effect of the strip link, the maximum width of the traverse is limited as shown by the AC line from the start of winding to φB, and the amount of edge breaking is also reduced as shown by Δl. As shown enlarged in Figure 2b, the maximum width of the traverse is limited up to the φB angle and varies along M''. It consists of a portion N _F and a zigzag valley portion N _C. If there is no limit on the maximum width of the traverse and the selvage is also performed between M and M', the line N becomes as shown by the dotted line, N _F
The ratio of and N _C remains constant. However, since the maximum width of the traverse is limited to a predetermined position and changes along M'', N _F gradually becomes smaller, and N _F and N _C
The ratio gradually changes and becomes constant after φB. In this way, the combination of the selvedge breaking action and the limit on the maximum width of the traverse allows the selvedge breaking ratio to be adjusted to a desired value, and the invention of this application achieves this with a relatively simple device. I was able to do that.

Embodiment (1) Figure 1 is an overall layout diagram of the device of this invention, in which 1 is a package, 2 is a cradle arm,
3 is a friction roller, 4 is a traverse guide, 6 is a traverse drum, 42 is a cam plate, 4
2' indicates a traverse groove, and 45 indicates a feedback arm.

FIG. 3a is an explanatory view of the mechanism of the selvedge breaking device of this invention, and shows the state at the beginning of winding.

The cam plate 4 is rotatable about the fixed shaft 41.
2 is supported, and the base end support shaft of the traverse guide 4 is fitted into the groove 42', and the traverse width changes depending on the inclination of the cam plate. The cradle arm 2 is connected to the cradle arm 2 via the feedback arm 45 at one end of the selvage link 44 rotatably supported by a shaft 43 attached to one end of the cam plate.
(Fig. 1).

On the other hand, a cam plate strip link 47 rotatably supported by a fulcrum shaft 46 fixed to the frame of the traverse unit is connected to a feedback arm 45 via a link 48. The cam surface 49 of the selvage link 44 is always pressed against the selvage cam 51 by the spring 50,
Moreover, the ear breaking cam 51 is supported by the shaft 53 of the ear breaking bar 52. The cam 51 is a tension coil spring 54
and the step 55 keeps the cam surface 56 generally perpendicular to the axis of the scroll cam (not shown).

(2) At the beginning of winding, the predetermined winding width (between A-A' in Figure 2a) is reached at the position where the cam plate 42 contacts the stopper 57 of the cam plate strip link 47.
Set it so that

At the home position H on the left side of the ear breaking bar 52, the cam surfaces 56 and 49 are in contact, and the tension spring 54 is in contact with the cam surfaces 56 and 49.
The position is such that the ear breaking cam 51 can rotate clockwise against the force.

The ear breaking bar 52 is at home position H for ear breaking.
When moving to the right from 53' to 53', the ear breaking link 44 does not move until the shaft 53 reaches the position 53' (Fig. 3b), and then the position of the shaft 53 changes from 53' to 53''.
Perform the ear breaking to the position shown in (Figure 3 a). That is, the position of the shaft 53 from 53 to 53' is N _F in Fig. 2.
The area from 53' to 53'' is the N _C part.The arrow R represents the direction of the selvage-breaking operation of the selvedge-breaking bar 52.As mentioned above, this operation does not require any particular adjustment and may be performed at a constant cycle. .

(3) When package 1 gradually becomes thicker, the first
The cradle arm 2 in the figure rotates clockwise,
The feedback arm 45 retreats as shown by arrow D, and the ear breaking link 44 retreats along the cam surface 56 (that is, it descends as shown by arrow D in FIG. 3a).
The cam plate 42 rotates clockwise about the fixed shaft 41. (In other words, the right end is lower in Fig. 3.) Furthermore, the cam plate stop link 4
7 is also pulled by the feedback arm 45 via a link 48 and rotates clockwise about a shaft 46. At that time, the stopper 57 is approximately (46-
57)/(46-58) until the stopper 47 and cam surface 42 reach the position shown in FIG.
are in contact with each other, restricting the counterclockwise return of the cam surface and limiting the maximum width of the traverse. From the position shown in FIG. 4, the stopper 47 and the cam surface 42 are separated from each other, resulting in the state shown in FIG. 5. In other words, the state from Fig. 3 to Fig. 4 is the state up to φB in Fig. 2, and the maximum width of the traverse is AC (i.e., line M''). ), the restriction of the stopper 57 is removed, and the selvage breaking operation between the lines M and M' in FIG. 2 is performed.

In FIGS. 3 to 6, a two-dot chain line 51'' is the position of the edge breaking cam 51 corresponding to the position of the shaft 53''. Further, a two-dot chain line 44' indicates the position of the selvedge link 44 corresponding to the cam surface of the cam 51''.

Effects The structure of this device is as described above,
To obtain a selvage breaking device which can provide an appropriate selvage ratio in a selvage breaking operation with a relatively simple structure in a cheese winding thread winding machine.

[Brief explanation of the drawing]

Figure 1 is an overall layout of the device of this invention, Figure 2a is a diagram showing changes in the amount of selvedge of the package cage, and Figure 2
Figure b is an enlarged view, Figure 3a is an explanatory diagram of the mechanism of the device of this invention in the state at the beginning of winding, Figure 3b is an explanatory diagram of the state in which the ear breaking bar has moved slightly, and Figure 4 is an explanatory diagram of the state in which the package cage is in position. Figure 2 shows the state when it is wound up to φB, Figure 5 shows the state when the diameter is larger than φB, Figure 6 shows a known selvedge breaking device, Figure 7a,
b, c are operational diagrams of the known device. Explanation of symbols, 1...Package, 2...Cradle arm, 3...Friction roller, 4...
Traverse guide, 6...Traverse drum, 4
1...Fixed shaft, 42...Cam plate, 43...Shaft, 4
4...Ear break link, 45...Feedback arm, 46...Fully shaft, 47...Stop link, 48...Link, 49...Cam surface, 50...
Spring, 51...Ear breaking cam, 52...Ear breaking bar, 53...Shaft, 54...Tension coil spring, 5
5...stage, 56...cam surface, 57...stopper, 58...shaft.

Claims (1)

[Scope of utility model registration request] In the selvage breaking device of a yarn winding machine, which consists of a cam plate that rotates around a fixed shaft, a traverse guide that changes the amount of traverse by the swinging of this cam plate, and a selvage breaking bar, etc. A selvage link is rotatably supported on the shaft, and this link is connected at one end to a cradle arm via a feedback arm, and is rotatably supported on a fulcrum shaft fixed to the frame of the traverse unit. The cam plate stop link is connected to the feedback arm via another link, and the cam surface of the selvage link is rotatably supported by the selvage bar, and the cam surface is connected by a tension spring. A selvage breaking device for a yarn winding machine, characterized in that the selvage breaking device is engaged with a selvedge breaking cam that is pulled to the side.