JP2003081532A - Bobbin holder - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bobbin holder and a yarn winding device capable of winding a yarn at a high speed without enlarging the diameter of the bobbin. SOLUTION: This bobbin holder has a holder member 2, in which a bobbin 11 is to be fitted, a support member 4 for supporting the holder member freely to turn, and a motor 7 for driving the holder member. The holder member is provided with a pushing means for pushing the bobbin to be fitted in the holder member to a motor side and a positioning member 2a for positioning the bobbin to be pushed.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a bobbin holder used for winding a linear body such as a yarn or a steel wire, and more particularly to a bobbin holder suitable for winding at a high speed.

[0002]

2. Description of the Related Art In recent years, further improvement in productivity and cost reduction have become important issues in the synthetic fiber manufacturing process. In order to solve this problem, in the bobbin holder used in the yarn winding device, further speedup is promoted, a large number of bobbins can be attached at one time, and a cheaper small-diameter bobbin can be used. A so-called small-diameter long type that can be used is desired.

The bobbin holders used in recent yarn winding devices have been increased in speed, length, and diameter in accordance with the above demands, and the winding speed has a low critical speed (so-called natural vibration). Number) and the vibration energy is large and cannot be overcome. It is mainly used in the rotational speed range lower than the higher critical speed.

As such a conventional bobbin holder, for example, one disclosed in Japanese Patent Laid-Open No. 2-225268 has been proposed, and a general structure of this bobbin holder is as shown in FIG.

That is, in the conventional bobbin holder 1, the holder member 2 is fixed to the bobbin holder shaft 3 which is directly connected to the motor shaft 8 via the coupling 12, and a plurality of (8 in the figure) the outer periphery of the holder member 2. Of the elastic ring 45, a cylindrical spacer 46 for positioning the elastic ring 45, a pressing member 41 for pressing each elastic ring 45 in the right direction in the drawing, and a pressing force in the right direction for the pressing member 41. A pressing mechanism including a disc spring 44 and a piston shaft 42 to be applied is provided. A supply hole 8a for supplying compressed air is provided at one end of the motor shaft 8.
Further, through holes 8b and 3a for supplying compressed air are provided so as to communicate with the shaft center of the motor shaft 8 and the bobbin holder shaft 3.

When the bobbin holder 1 having the above structure holds the bobbin 11, the pressing member 41 is moved to the right in the drawing by the pressing force of the disc spring 44 (expanding force to the right in the drawing), and each elastic member is elastically moved. The ring 45 is compressed from both sides. At this time, the bobbin 11 is gripped by the elastic rings 45 being radially increased and deformed.

On the other hand, when releasing the grip of the bobbin 11, compressed air is supplied from a compressed air source (not shown) to the supply hole 8
By supplying from a to the chamber 5a through the through holes 8b and 8a, the piston 42 is driven in the left direction of the drawing against the pressing force of the disc spring 44, and at the same time, the pressing member 41 is moved in the left direction of the drawing. The increased diameter deformation of the elastic ring 45 is released.

The element member having the greatest influence on the specification of the bobbin holder 1 is the holder member 2 which is the longest among the constituent elements. When the unit is Hz, the critical speed Nc of such a cylindrical member is generally expressed by the following equation (1), and a large value thereof increases the critical speed of the entire Bonholder.

Nc∝ [(I / A) ^1/2 / L ² ) × (E / ρ) ^1/2 (1) where I is the second moment of area, L is the total length of the holder member, A is the cross-sectional area, E is the elastic modulus, and ρ is the specific gravity. If the outer diameter of the cylinder is Do and the inner diameter is Di, then I∝ (D
Since there is a relationship of o ⁴ −Di ⁴ ) and A∝ (Do ² −Di ² ), the equation (1) is expressed by Nc∝ [(Do ² + Di ² ) ^1/2 / L ² ] × (E / ρ) ^{1 / 2}・ ・ ・ (2) can be transformed.

As a means for improving the critical speed Nc, as disclosed in JP-A-8-175753,
An approach to increase Do in the above equation (2) has been proposed. This is because by providing a spring member inside the elastic ring 45 described above, the elastic ring 45 is thinned without impairing the gripping performance of the bobbin, and the outer diameter of the holder member is increased without changing the size of the bobbin to be fitted. It was possible.

[0011]

However, the bobbin holder described above is the same as the conventional one in that it has a bobbin holding mechanism using an elastic ring, and naturally there is a limit in increasing the outer diameter of the holder member. Further, these elastic rings require periodical replacement or repair as consumables, but since they have spring members, there is a problem that the manufacturing cost is higher and the running cost is higher than in the past.

Therefore, in the present invention, the bobbin can be reliably gripped without using the elastic ring, thereby increasing the outer diameter of the holder member to a value as close as possible to the inner diameter of the bobbin to be fitted. Therefore, it is an object of the present invention to provide a bobbin holder capable of improving the dangerous speed and reducing the running cost by reducing the consumables.

[0013]

SUMMARY OF THE INVENTION To achieve the above object, the present invention comprises a holder member on which a bobbin is fitted, a support member for rotatably supporting the holder member, and a motor for driving the holder member. The holder member is characterized by including a pressing means for pressing the bobbin fitted in the holder member toward the motor side, and a positioning means for positioning the pressed bobbin.

[0014]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of a bobbin holder according to the present invention will be described below with reference to the drawings.

FIG. 1 is a vertical sectional view showing an embodiment of a bobbin holder according to the present invention. For simplification, the same members as those in FIG. 9 showing the conventional example are designated by the same reference numerals. In FIG. 1, a bobbin holder 1 is generally equipped with a bobbin 11 for rotating a holder member 2, a chuck mechanism 5 for firmly holding the bobbin 11 on the holder member 2, and a holder member 2 fixed and integrated with the holder member 2. It is composed of a bobbin holder shaft 3 that rotates in a rotating manner, a support 4 that rotatably supports the bobbin holder shaft 3 via a bearing 6, and a motor 7 that rotates the holder member 2.

The support 4 and the motor 7 are fastened together so as to sandwich the frame 9, and the bobbin holder shaft 3 is connected to the motor shaft 8 via the coupling 12, so that the holder 7 is driven by the driving force of the motor 7. It can be rotated.

Although the structure of the chuck mechanism 5 will be described in detail later, in this figure, the pressing member 13 provided at the end portion of the holder member 2 opposite to the motor has a diameter larger than the inner diameter of the bobbin 11, and It is shown that an axial pressing force is applied to the bobbin 11 on the motor 7 side and the bobbin 11 is gripped between the bobbin 11 and the positioning means 2a for positioning the bobbin to be pressed which is provided at the motor side end of the holder member 2. ing.

In FIG. 2, the bobbin holder 1 shown in FIG.
2 shows the operation when releasing 1. At the same time that the pressing member 13 moves to the motor side of the holder member 2, the pressing force applied to the bobbin is released, and further, the diameter is reduced to be smaller than the inner diameter of the bobbin. At this time, the gripping force that fixed the bobbin disappears, and the bobbin can be pulled out.

FIG. 3 is a schematic front view showing the operation of the pressing member 13 in the bobbin holder 1 of FIG. Pressing member 13
Is composed of four pressing bodies 13a, 13b, 13c and 13d, and FIG. 3A shows a state in which the bobbin is held by expanding the holder member 2 about the rotation axis.
In addition, FIG. 3B shows a state in which the bobbin can be released by reducing the diameter around the rotation axis of the holder member 2.

In this embodiment, the pressing member 13 is composed of four pressing members of the same shape, but the effect of the present invention is 3
It is also possible to obtain it by constructing the pressing members in the number of 5, 5 or more.

Next, the detailed structure of the chuck mechanism 5 will be described with reference to FIG. The chuck mechanism 5 generally includes the pressing member 1.
3, pressing members 13a to 13d, pressing means for pressing the pressing member 13 against the bobbin 11, and pressing member 1
It comprises a diameter reducing means for reducing the diameter of 3 and a diameter increasing means for increasing the diameter of the pressing member 13.

Elastic members 48 are attached to the outer periphery of the pressing member 13 at a plurality of positions that come into contact with the holder member 2 so as to absorb the impact when separating or contacting the holder member 2.

The pressing means mainly comprises a piston shaft 14 provided inside the holder member 2 and a first compression spring 19 loosely fitted to the piston shaft 14, and the piston shaft 1
4 is a large diameter portion 14 having an outer diameter substantially equal to the inner diameter of the holder member 2.
a large diameter portion 14a is supported inside the holder member 2 via an O-ring 47 to form the chamber 5a and is fixed to the inside of the holder member 2 with a set screw. The plate 18 restricts the rotation direction.

As means for restricting the rotation direction of the piston shaft 14, the fixed disc 18 and the piston shaft 1 are used.
A means for forming a two-sided width on both sides and fitting them together is simple and preferably used.

The first compression spring 19 is the piston shaft 1
At the same time as being loosely fitted to the outer circumference of 4, the fixed disk 18 and the large diameter portion are provided. With this configuration, the first compression spring 19 generates a force that moves the piston shaft 14 to the right side of the drawing with the fixed disk 18 fixed inside the holder member 2 using a set screw as a base point.

Further, a movable annular body 17 having an L-shaped cross section and a second compression spring 20 are loosely fitted around the outer periphery of the piston shaft 14, and the movable annular body 17 is fixed by the second compression spring 20. A spreading force to the left in the figure acts on the disk 18 as a starting point.

Here, the spring force of the first compression spring 19 is
It is essential that the second compression spring 20 be configured so that it is always larger than the spring force of the second compression spring 20.

A flange portion 14b is formed on the outer periphery of the piston shaft 14 at a position adjacent to the left side of the movable annular body in the figure. The flange portion 14b and the movable annular body 17 are arranged in the left direction of the figure. It is configured so that it can come into contact with the pressing member 13 when moved to. The collar portion 14b is fixed to the piston shaft 14 so as to move integrally therewith, but it can be detached when disassembling and assembling.

The means for reducing the diameter of the pressing member 13 mainly has a tapered surface, and the diameter reducing member 15 fixed inside the holder member 2 using a set screw and the pressing member 13 are shown in the left side of the drawing. It is composed of a moving means for moving toward. The means for moving the pressing member to the left in the figure is nothing but the means for moving the flange portion 14b of the piston shaft 14 to the left, and more specifically, in FIG. 8
Of the first compression spring 19 from the compressed air supply hole 8a provided at the right end of the first compressed spring 19 through the holes 8b and 3a communicating with the shaft center of the motor shaft 8 and the bobbin holder shaft 3, respectively. Overcome strong spring force, piston shaft 14
Is moved to the left in the figure.

The means for increasing the diameter of the pressing member 13 has a taper surface and has a diameter increasing member 16 fixed to the end of the piston shaft.
And means for moving the diameter increasing member 16 to the right in FIG. The means for moving the diameter-increasing member 16 to the right is a means for moving the piston shaft 14 to the right in the figure, which is exactly the same as the pressing means.

Next, regarding the shape of each main member,
A detailed explanation will be given. FIG. 5 shows a schematic perspective view of the pressing bodies 13a to 13d forming the pressing member 13. In this embodiment, since the pressing body is composed of four pieces, it is roughly shaped like a cylindrical member cut by 90 ° and has a large diameter portion for pressing the bobbin. It has taper surfaces 21 and 22 respectively facing the outer peripheral direction and the inner peripheral direction, and further, adjacent to the taper surface 21, a phase stop surface 23.
have. Further, it is preferable to provide screw holes 24 for attaching weights for correcting the balance when the bobbin holder 1 is assembled in the bobbin holder 1 at positions equidistantly in the circumferential direction when gripping the bobbin.

FIG. 6 is a schematic perspective view of the diameter reducing member 15.
The diameter reducing member 15 has a ring shape in which four projecting portions extending in the axial direction are equally arranged in the circumferential direction. A screw hole is provided on the outer peripheral side of the protruding portion, so that the holder member 2 is fixed. Further, the inner peripheral surface of each protrusion has a taper surface 25 having the same angle as the taper surface 21 of the pressing bodies 13a to 13d, and the side surface of the protrusion has a phase stop surface 2
6 is configured to come into contact with the phase stop surface 23 of the pressing body. This is the pressing body 13 against the holder member 2.
This is to prevent the phase in the rotation direction of a to 13d from changing, and when the phase shifts, the bobbin position shifts and the winding itself may not be performed.

FIG. 7 shows a schematic perspective view of the diameter increasing member 16.
Four taper surfaces 28 having the same angle as the taper surface 22 of the pressing bodies 13a to 13d are provided on the outer peripheral side, and a hole 29 for attaching to the piston shaft is provided at the center. Although omitted in this figure, means for preventing the phase shift as described above is required, and it is preferable to provide a key groove in both the diameter increasing member 16 and the piston shaft 14 and insert a key material between them. Therefore, it is better to stop rotation.

[0034]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The operation of each part when gripping or releasing the bobbin will be described in detail with reference to FIGS. 1 and 2 again as an embodiment.

When the bobbin is replaced, the compressed air is supplied to the compressed air supply hole 8a from the state in which the bobbin is gripped as shown in FIG. 1 and the state shown in FIG. 2 is obtained. At this time, the compressed air flows into the chamber 5a through the through holes 8b and 3a at the center of the motor shaft and the bobbin holder shaft, resisting the spring force of the first compression spring 19 and moving the piston shaft 14 to the left in the drawing. Move to.
With the movement of the piston shaft 14, the pressing force acting on the bobbin 11 on the side of the positioning means 2a provided on the holder member 2 is released. Further, the flange portion 14b provided on the piston shaft 14 contacts the pressing member 13, and the pressing member 13
To the left. At this time, the first tapered surface 21 of the pressing bodies 13a to 13d forming the pressing member 13 abuts on the tapered surface 25 of the diameter reducing member, and as the piston shaft 14 further moves to the left, both tapered surfaces are moved. Along each of the four pressing bodies, the four pressing bodies approach the axial center of the holder member 2, and the diameter of the pressing member 13 is reduced. When the pressing member 13 has a diameter smaller than the inner diameter of the bobbin 11, the piston shaft 1
4 and the fixed disc 18 contact each other, and the piston shaft 14 is prevented from moving any further.

In this way, when the pressing member 13 has a diameter smaller than the inner diameter of the bobbin 11, the bobbin can be freely removed,
Further, it becomes possible to fit a new bobbin.

After installing a new bobbin, until then,
The bobbin is gripped from the state of FIG. 2 to the state of FIG. 1 by cutting off the compressed air supplied from the compressed air supply hole 8a and exhausting the compressed air.

At this time, first, the piston shaft 14 starts to move to the right in the figure by the expanding force of the first compression spring 19. Collar 14b of piston shaft that was in contact until then
Then, the pressing body separates, and this time, the tapered surface 28 of the diameter increasing member 16 and the second tapered surface 22 of the pressing body come into contact with each other. Further, the moving annular body 17 and the pressing bodies 13a to 13d start contact with each other. Since the moving annular body 17 regulates the axial movement of the pressing body by the spring force of the second compression spring 20, each of the pressing bodies 13a to 13d moves to the right of the diameter increasing member 16. Along with the movement, the holder member 2 is gradually moved in the outer diameter direction, that is, the pressing member 13 is increased in diameter.
When the piston shaft 14 moves to the right, the pressing body 13
The a to 13d abut on the inner peripheral surface of the holder member 2 via the elastic body 48, and the large diameter portion of the pressing body projects larger than the inner diameter of the bobbin. However, at this time, I have not touched the end face of the bobbin yet. When the piston shaft 14 further moves, the pressing member 13 starts to move in the axial direction, comes into contact with the bobbin end surface, and the spring force of the first compression spring 19 and the spring force of the second compression spring 20 are increased. The difference acts as a pressing force.

In this embodiment, the spring forces of the first compression spring 19 and the second compression spring 20 are about 1500N and 300N, respectively, at the position shown in FIG. Therefore, at this time, the pressing force applied to the bobbin end portion for gripping the bobbin takes a value almost close to 1200 N which is the difference between the two.

Further, since the speed at which the pressure bodies 13a to 13d operate is determined by the exhaust speed of the compressed air from the chamber 5a, it is preferable to adjust the exhaust speed by narrowing.

By adopting the structure of the bobbin holder of the present invention, the elastic ring which has been used conventionally becomes unnecessary, and the outer diameter of the holder member can be correspondingly increased.
Specifically, in the past, in order to grip a bobbin having an inner diameter of 94 mm, the outer diameter of the holder member was set to 80 mm because of the thickness of the elastic ring, but by using the present invention, the outer diameter of the holder member is It is possible to increase the inner diameter of the bobbin to the limit, and when the thickness is calculated to be 3 mm, the second moment of area is simply about 1.6 times, and the rigidity of the holder member can be remarkably increased. As a result, it is possible to raise the critical speed of the bobbin holder. With the conventional bobbin holder, the maximum speed is about 5000 m / min for a type that can mount eight bobbins with an inner diameter of 94 mm, an outer diameter of 110 mm and a length of 150 mm. On the other hand, with the bobbin holder of the present invention, the maximum speed reached up to 7000 m / min. In this example, a bobbin made of resin was used for the evaluation.

The bobbin holder of the present invention and the winding device using the bobbin holder described above can be used, for example, of winding a linear body such as a yarn or a steel wire on a bobbin. It can also be suitably applied to the winding of sheet materials such as resin films, woven and knitted fabrics, non-woven fabrics and paper.

Among them, as shown in FIG. 8, the yarn winding device using the bobbin holder of the present invention roughly includes the bobbin holder 1, the touch roll 31 which rotates while being in contact with the package, and the yarn traversing. It is composed of the traverse device 32 and a frame supporting them, and can be used more preferably.

Further, as a method of manufacturing a yarn package using this yarn winding device, a spinneret 33, an air guide 34, a take-up roller 35, as shown in FIG.
It can be more suitably implemented by applying it to the yarn manufacturing process including the yarn winding device 30, the yarn guides 37 and 39, the tension meter 38, and the yarn winding device 30.

[0045]

As described above, the bobbin holder of the present invention has a holder member into which the bobbin is fitted, a support member that rotatably supports the holder member, and a motor that drives the holder member. Since the holder member includes a pressing unit that presses the bobbin fitted in the holder member toward the motor, and a positioning unit that positions the pressed bobbin, the following excellent operational effects are obtained. Obtainable. (1) It is possible to raise the critical speed of the bobbin holder to a high-speed area, and further, when manufacturing the holder member,
Since no special processing is required, the speed-up of the winding device can be realized at extremely low cost. Further, even with respect to the existing winding device, it is possible to cope with high-speed winding only by exchanging the holder member and the chuck mechanism, so that the equipment can be renewed with a small modification cost. (2) Since the bobbin inner diameter does not become large, it is not necessary to modify the transportation equipment after the winding device, and the bobbin cost is reduced compared to the case where the bobbin inner diameter is made large and the winding speed is increased. (3) Compared to the conventional bobbin holder that uses an elastic ring to hold the bobbin, the number of parts is smaller, so the manufacturing cost can be reduced, and periodic elastic ring replacement is not required, so running cost is reduced. Can be reduced, and further, the maintenance work can be reduced.

[Brief description of drawings]

FIG. 1 is a schematic vertical cross-sectional view showing an example of a bobbin holder of the present invention.

FIG. 2 is a schematic vertical cross-sectional view showing the bobbin holder of FIG. 1 when a bobbin is released.

FIG. 3 is a schematic front view showing the operation of the pressing member in the bobbin holder of FIG.

FIG. 4 is a schematic vertical sectional view showing a main part of the bobbin holder shown in FIG.

5 is a schematic perspective view of a pressing body included in the bobbin holder of FIG.

FIG. 6 is a schematic perspective view of a diameter reducing member included in the bobbin holder of FIG.

FIG. 7 is a schematic perspective view of a diameter increasing member included in the bobbin holder of FIG.

8 is an explanatory view of a yarn winding device and a yarn manufacturing process of the present invention including the bobbin holder of FIG. 1. FIG.

FIG. 9 is a schematic vertical sectional view showing a conventional bobbin holder.

[Explanation of symbols]

1: Bobbin holder 2: Holder member 2a: Positioning means 3: Bobbin holder shaft 3a: Communication hole 4: Support 5: Chuck mechanism 6: Bearing 7: Motor 8: Motor shaft 8a: Pneumatic supply hole 8b: Communication hole 9: Frame 10: Chamber 11: Bobbin 12: Coupling 13: Pressing member 13a-d: Pressing body 14: Piston shaft 14a: Large diameter part 14b: collar part 15: Diameter reducing member 16: Increasing member 17: Moving ring 18: Fixed disk 19: First compression spring 20: Second compression spring 21: First tapered surface 22: Second tapered surface 23: Non-rotating surface 24: Balance correction hole 25: Tapered surface 26: Anti-rotation surface 27: Non-rotating hole 28: Tapered surface 29: Hole 30: Thread winding device 31: Touch roll 32: Traverse 33: Spinneret 34: Air guide 35: Collection roll 36: Collection roll 37: Guide 38: Tensiometer 39: Guide 40: Thread 41: Front lid 42: Piston shaft 43: Fixed disk 44: compression spring 45: Elastic ring 46: Spacer 47: O ring 48: Elastic body

Claims (8)

[Claims] 1. A holder member on which a bobbin is fitted, a support member for rotatably supporting the holder member, and a motor for driving the holder member, wherein the holder member is fitted on the holder member. A bobbin holder comprising: a pressing unit that presses the mounted bobbin toward the motor side; and a positioning unit that positions the pressed bobbin. 2. The bobbin holder according to claim 1, wherein the pressing means includes a pressing member for the bobbin, and a diameter reducing means and a diameter increasing means for the pressing member. 3. The pressing member has at least three pressing members that are equally arranged in the circumferential direction of the holder member and are movable in the radial direction and the axial direction of the holder member. The bobbin holder according to claim 2. 4. The bobbin holder according to claim 3, wherein each of the pressing bodies has a first taper surface in an outer peripheral direction of the holder member and a second taper surface in an inner peripheral direction of the holder member. 5. The diameter reducing means has a tapered surface parallel to the first tapered surface on its inner surface, and the diameter reducing member fixed inside the holder member is in contact with these tapered surfaces. The bobbin holder according to any one of claims 2 to 4, comprising a moving unit that moves the pressing body in a contacting direction. 6. A diameter increasing member having an outer surface having a tapered surface parallel to the second tapered surface, and a moving means for moving the diameter increasing member in a direction in which the tapered surfaces abut. The bobbin holder according to claim 2, wherein the bobbin holder is formed of: 7. A yarn winding device having the bobbin holder according to any one of claims 1 to 6. 8. A method of manufacturing a yarn package, which comprises using the yarn winding device according to claim 7.