JPH05294559A - Spun tarn winder - Google Patents

Abstract

PURPOSE:To provide a spun yarn winder which can reduce vibration upon resonance of an elevatable frame, and which can be operated in a wide wind-up speed range. CONSTITUTION:In a spun winder in which a body frame 2 supports a frame 11a for holding a touch roller 11 adapted to make rolling contact with bobbin holders 5, 6 carrying bobbins B on which packages P are formed, is attached thereto with a dynamic vibration absorber 15 in which an elastic body 16 and a weight 17 are arranged in series in a cantilever manner at the front end of the frame 11a, in the mentioned order, so as to restraining resonance.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a spinning winder for winding a yarn spun from a spinning machine at a high speed, and more particularly to a spinning winder in which the vibration of the lifting frame during resonance is reduced.

[0002]

2. Description of the Related Art First, a conventional take-up winder will be described with reference to FIGS. 6 is a side view and FIG. 7 is a front view.

In FIGS. 6 and 7, the take-up winder 1 is
A turret disc 4 that rotates around a horizontal axis 3 with respect to the main body frame 2, two bobbin holders 5 and 6 protruding from the turret disc 4, and the bobbin fixed to the back surface of the turret disc 4. Induction motors 7 and 8 that rotationally drive the holders 5 and 6, an elevating frame 10 that is vertically moved up and down by being guided by columns 9 in the main body frame 2, and supported by a first frame body 10 a of the elevating frame 10. Touch roller 11 and traverse device 12 supported by the second frame 10b of the elevating frame 10.
It is mainly composed of and. That is, the bobbin holders 5 and 6 are indirectly provided on the body frame 2 via the turret disc 4. The weight of the entire lifting frame 10 that supports the touch roller 11 and the traverse device 12 is supported by the contact pressure cylinder 13 provided on the side of the lifting frame 10, and the difference between this weight and the lifting force of the contact pressure cylinder 13 is touched. The contact pressure of the roller 11 with respect to the package P is set. In addition, B is a bobbin, P is a package wound around the bobbin, Y is a yarn from a spinning machine, 2
Reference numeral a denotes a fixed arm portion that projects from the main body frame 2 and has an operation panel at its tip.

Next, an outline of the winding operation of the take-up winder 1 will be described. In FIG. 6, an inverter 21 for controlling the number of revolutions is connected to the induction motors 7, 8 of the bobbin holders 5, 6 and a pulse generator 22 for detecting the number of revolutions (that is, yarn speed) is provided on the touch roller 10. Has been. Then, the setting signal f2 of the winding speed signal generator 23 is compared with the signal f1 of the pulse generator 22, and the comparator 2
An instruction is given from 4 to the inverter 21 to maintain a predetermined winding speed. That is, as the package P becomes thicker and thicker, the number of rotations of the bobbin holders 5 and 6 decreases. When the package P is fully wound, the turret disc 4 is rotated by 180 °, the bobbin holder 6 of the fully wound package P is at the standby position shown, and the empty bobbin B is moved.
The bobbin holder 6 becomes the winding position shown in the figure, and the yarn is passed from the fully wound package P to the empty bobbin B, and the winding is continuously performed. Then, the bobbin holder 6 of the fully wound package P is gradually decelerated and stopped, and the fully wound package P and the empty bobbin B are replaced.

In the above-described conventional take-up winder, the bobbin holders 5 and 6 during winding change their rotational speed in a wide range from the beginning to the end of winding. The touch roller 11 that applies an appropriate contact pressure to the package P wound around the bobbin B mounted on the bobbin holders 5 and 6 is affected by this rotation speed. That is, the bobbin holders 5 and 6 serve as vibration sources, and the lifting frame 1 that holds the touch roller 11 is used.
0 causes a resonance phenomenon. Therefore, conventionally, the elevating frame 10 has been designed so that the natural frequency of the elevating frame 10 is equal to or lower than the rotational frequency of the bobbin holders 5, 6.

[0006]

However, in recent years, the use of a spinning winder in a wide range from low speed to high speed has been demanded, and the range of the rotational frequency of the bobbin holders 5 and 6 tends to be widened. For example, in wide range winding from low speed 2000 m / min to high speed 6000 m / min, the rotation frequency of the bobbin holders 5 and 6 is at least 24 Hz and at most 290.
It reaches as high as Hz. As described above, it is practically difficult to design the elevating frame 10 that does not have a natural frequency in a wide range of rotational frequencies, which limits the operating speed range of the take-up winder. Had.

The present invention has been made in view of the above problems of the prior art, and an object of the present invention is to reduce vibration at the time of resonance of the elevating frame and to achieve a wide range of winding speeds. The present invention intends to provide a take-up winder that enables the above operation.

[0008]

In order to achieve the above object, the spinning winder according to the present invention is provided with a bobbin holder for mounting a bobbin on which a package is wound and mounted on a main body frame, and rolls on the bobbin holder. In a take-up winder in which a frame holding a touch roller is supported by the main frame in a cantilevered manner, a dynamic vibration absorber further arranged in series in a cantilevered manner with a rubber elastic body and then a weight at the tip of the frame. Is attached.

[0009]

[Function] The cantilevered frame has a larger resonance amplitude toward the tip,
A dynamic vibration absorber in which rubber elastic bodies and then weights are arranged in series in order to absorb the resonance amplitude most efficiently.

[0010]

Embodiments of the present invention will be described below with reference to the drawings. 1 is a side view of a take-up winder of the present invention, and FIG. 2 is a front view.

In FIGS. 1 and 2, the same reference numerals are given to the parts that operate in the same manner as in FIGS. 6 and 7, and the description thereof will be omitted. In FIGS. 1 and 2, FIGS.
The difference is that the dynamic vibration absorbers 15 arranged in series in a cantilever manner in the order of the rubber elastic body 16 and the weight 17 are attached to the tip of the first frame body 10a of the cantilever lifting frame 10.

The dynamic vibration reducer 15 has a simple structure composed of two rubber elastic bodies 16 and a weight 17. A normal iron block is used for the weight 17. As the rubber elastic body 16, a commercially available one is generally used as an anti-vibration rubber, and in the illustrated example, mounting bars 16a and 16b independent from each other are embedded in the left and right. The rubber elastic body 16 is attached to the tip of the first frame 10a by the attachment bar 16a, and the weight 17 is attached to the rubber elastic body 16 by the attachment bar 16b. That is,
The dynamic vibration reducer 15 is further attached to the tip of the cantilevered first frame body 10a in a cantilevered manner. With such a cantilever shape, it can be easily attached to the tip of the first frame body 10a, and the dynamic vibration absorption efficiency described below becomes high. The number of rubber elastic bodies 16 is not limited to two, but may be an appropriate number.

As described above, when the dynamic vibration reducer 15 is further attached to the tip of the cantilevered first frame body 10a in a cantilever manner, a protruding portion is formed, so that the whole dynamic vibration reducer 15 is formed. It is preferable to cover with a cover 18. Further, if the space inside the cover 18 is made a closed space, the rubber elastic body 16 which is easily deteriorated is shielded from the external atmosphere.

A lifting frame 10 to which a dynamic vibration reducer 15 is attached
The model will be described with reference to FIG. The weight 17 has a mass m, the elastic rubber 16 serves as a spring having a spring constant k and a damper having a damping constant c, and the elevating frame 10 serves as a spring having a spring constant K determined by the weight of the mass M and its supporting structure. In this model, the optimum design condition of the dynamic vibration reducer 15 satisfies the following formulas and formulas. Optimal natural frequency = (1 / (1 + μ)) x Ω _n ... formula Optimal damping ratio = (3μ / 8 (1 + μ)) ^1/2 ... where μ: Iron block and lifting Frame mass ratio (m / M) Ω _n : Natural frequency of the elevating frame ((K / M) ^1/2 )

A vibration frequency response pattern of the elevating frame 10 to which the dynamic vibration reducer 15 is attached will be described with reference to FIG. A dotted line shows a pattern when the dynamic vibration reducer 15 is not attached, and a solid line shows a pattern when the dynamic vibration reducer 15 is attached. The sharp resonance phenomenon changes into a gradual increase in the trapezoidal amplitude. The larger the mass ratio (m / M) between the weight and the lifting frame, the lower the amplitude. But,
The amplitude decreases significantly until the mass ratio is 0.1,
In particular, even if it exceeds 0.2, it does not decrease so much and only the whole lifting frame becomes heavy. Therefore, the most effective mass ratio is 0.1 to 0.2.

When the above-mentioned optimum conditions are applied to an actual spinning winder, the iron block of the dynamic vibration reducer is about 5 to 10 kilograms. A dynamic vibration absorber of 5 kilograms on the lifting frame having a natural frequency of 44 Hz (the lifting frame is about 40 kg,
When the mass ratio is about 0.13) and nylon 6 is wound at 3800 m / min at the position shown in FIGS. 1 and 2, the amplitude of the elevating frame 10 is significantly reduced as shown in FIG. did.

When the above optimum conditions are applied to an actual spinning winder, the weight of the dynamic vibration reducer is about 5 to 10 kilograms. A 5 kg dynamic vibration absorber (elevation frame is about 40 kg, mass ratio about 0.13) is attached to the elevating frame having a natural frequency of 44 Hz at the position shown in FIGS. 1 and 2, and nylon 6 is 3800 m. The amplitude of the elevating frame 10 was significantly reduced when wound at a speed of / min.

In the above embodiment, the so-called spindle drive type in which the bobbin holder on which the bobbin is mounted is directly driven by the induction motor has been described as the spinning winder, but the present invention is mounted on the bobbin holder. It is also applicable to a so-called friction drive type in which a bobbin indirectly drives the bobbin by rollingly touching a touch roller which is driven. In addition, the bobbin change is not limited to the auto changer type in which the turret disc is rotated to automatically switch from the full package to the empty bobbin. The present invention can also be applied to a take-up winder of the type that performs.

[0019]

EFFECT OF THE INVENTION The spinning winder of the present invention is such that a cantilevered rubber elastic body and then a dynamic vibration absorber arranged in series in the order of weights are attached to the tip of the frame, and the resonance amplitude is large. Since the cantilevered frame body has a cantilevered structure at its tip, the dynamic vibration absorber most efficiently absorbs the resonance amplitude, so that the resonance can be suppressed by the dynamic vibration absorber having a simple structure. As a result, the restriction on the design of the natural frequency of the elevating frame is released, and it is possible to cope with a wider range of winding from low speed to high speed.

[Brief description of drawings]

FIG. 1 is a side view of a take-up winder according to the present invention.

FIG. 2 is a front view of the take-up winder of the present invention.

FIG. 3 is a model diagram of a vibration system.

FIG. 4 is a graph showing a pattern of vibration frequency response.

FIG. 5 is a graph showing the actual vibration of the lifting frame.

FIG. 6 is a side view of a conventional take-up winder.

FIG. 7 is a front view of a conventional take-up winder.

[Explanation of symbols]

 2 Body frame 5, 6 Bobbin holder 10 Lifting frame (frame body) 11 Touch roller 15 Dynamic vibration absorber 16 Rubber elastic body 17 Weight B Bobbin P package

Claims (1)

[Claims] A bobbin holder for mounting a bobbin on which a package is formed is provided on a main body frame, and a frame for holding a touch roller rolling on the bobbin holder is cantilevered by the main body frame. In the machine
A spinning winder, further comprising a dynamic elastic absorber arranged in series in a cantilever manner on the front end of the frame body in the order of a rubber elastic body and a weight.