JP3499299B2 - Stranded wire machine - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a twisting machine for twisting a plurality of filaments (hereinafter referred to as "elementary wires") such as a pair of communication cables or a quad to manufacture a twisted wire. Is.

[0002]

2. Description of the Related Art A twisting machine generally comprises a supply means consisting of a plurality of bobbins for supplying the wires, a twisting die for collecting the supplied wires into one, and a twisting means for twisting the wires. A winding means for winding the twisted strands (stranded wire) is provided, and a twisting means, an appropriate guiding means, a constant tension holding means, etc. are provided as necessary. As a method for twisting the strands,
A method of rotating the supply means and the winding means around their respective rotation axes, and rotating the supply means around the twisted wire axis and a method of rotating the winding means. There is a method in which a guide means such as an arc is provided at a portion for guiding the body to the winding means, and the guiding means is rotated around the winding means. Although it depends on the type of wire and the size of the rigidity, in general,
Better than anything.

Therefore, a conventional twisting machine will be described as an example. FIG. 6 is a diagram showing an example of a double twist type twisting wire machine. In FIG. 6, 10 is a supply means for supplying a plurality of strands W, 20 is a winding means for winding the twisted strands, that is, a twisting means for twisting the strands, and 40 is a constant tension holding device. A dancer roller as a means, 43 is a guide roller as a guide means, 50
Is a twisting die.

The supply means 10 is a supply bobbin 11
And a cradle 12 having a rotary shaft 13 at both ends for supporting a supply bobbin, an arcuate guide 15 rotatably provided around the cradle 12, a guide roller R1 and the like. The supply means 10 is integrated with four frame 17 Supported by. The wire W is paid out from the supply bobbin 11 along a guide roller R1 and a guide roller (not shown) provided on the arcuate guide, as described later in detail.
It is guided to the dancer roller 40 via the guide roller 16,
After being wound around the wheels 41 and 42 for 1 to 2 reciprocations, it is guided to the twisting die 50 through the guide roller 43. Although not shown, the dancer roller 40 and the guide roller 41 are arranged four in a horizontal direction corresponding to the four supply means 10, and guide four strands.

The four strands are assembled together by a twisting die 50. The gathered wires are twisted by the twisting means 30.

The twisting means 30 has a hollow shaft 3 at both ends.
An arcuate guide 33 and a guide roller 34 having 1, 32,
35, bearings 36 and 37, and timing pulleys 38 and 39
Consists of. The winding means 20 has an arcuate guide 33 through a bearing mechanism (not shown) provided in the hollow shafts 31, 32.
The cradle 21 is rotatably supported with respect to the cradle 21, a take-up capstan 22 attached to the cradle 21, a traverse mechanism 23, and a take-up bobbin 24. 70
Is a motor as a power source, which transmits power through the winding means, the twisting means, and the transmission mechanisms 71 to 76.

The gathered wires pass from the hollow shaft 38 of the twisting means 30 through the guide roller 34, and then the bow-shaped guide 33.
And is wound around the winding bobbin 24 through the guide roller 35, the hollow shaft 32, the take-up capstan 22, and the traverse 23. During this time, the rotation of the arcuate guide 33 causes twisting at two points of the guide roller 34 and the guide roller 35. Given.

Generally, in the case of producing a twisted wire having a desired pitch, in order to increase the twisting speed, it is necessary to increase the take-up speed as well as the rotation speed. In the wire machine, the arcuate guide is twisted twice for each rotation, and the weight of the arcuate guide, which is a rotating body, is light, so that the speedup is facilitated.

[0009] By the way, the twisting is added to the strands along with the so-called revolution of rotating the strands around the twist axis, and therefore twisting is required to eliminate this twist. For example, there is a case where the rigidity of the wire is large or a case where the electrical characteristics are affected by a pair of communication cables or a quad. The twisting is performed by rotating the supply means in the direction to eliminate the twist. Therefore, as described above, twisting is performed by rotating the arcuate guide 15 of each supply means 10 in the same direction as the arcuate guide 33 of the twisting means.

[0010]

However, as the manufacturing speed of the twisted wire is increased, the rotation speed of the arcuate guide 33, which is a twisting means, must be increased, and therefore, the arcuate guide 15 that is a twisting means is required. The rotation speed of must also be increased. When the rotation speed of the arcuate guide 15 is increased, the centrifugal force applied to the wire increases, which not only increases the axial component force of the wire, but also increases the frictional resistance between the wire and the arcuate guide or the guide roller with which the wire contacts. Since the bending resistance of the wire increases, the tension load accumulated in the axial direction of the wire (hereinafter referred to as "cumulative tension load") increases, and the wire cannot be drawn with the tension set by the dancer roller. , Slack occurs in the wire W in the supply means,
There is a problem that the strands are entangled and broken. Also, if the set tension of the dancer roller is increased, the slack of the strand W can be prevented, but the accumulated tension applied to the strands is increased as the set tension is increased. Therefore, there has been a problem that the strand is thinned beyond the elastic limit of the strand. It is an object of the present invention to solve the above problems, and to provide a twisting machine capable of increasing the production speed of a twisted wire without causing disconnection or thinning, and without using an expensive control device.

[0011]

In order to achieve the above object, a twisting machine according to claim 1 of the present invention comprises a plurality of supply means and a plurality of supply means supplied from each of the supply means through dancer rollers. A twisting means for twisting the wires,
In a twisting machine provided with a means for winding the twisted strands and a winding means, the dancer roller upstream side of the running path of each strand supplied from each supply means to the twisting means via the dancer roller. A tension assisting means is provided on the tension assisting means, and the tension assisting means is composed of a tension roller for winding a wire and a drive mechanism for driving the tension roller, and the wire tension at the wire entrance of the tension roller is accumulated on the upstream side of the tension roller. It is driven by the drive mechanism so that the tension is equal to or more than the tension and equal to or less than the elastic limit value of the strand, and the strand tension at the strand outlet of the tension roller is made lower than the strand tension at the inlet. It is a feature.

A twisting machine according to a second aspect is the twisting machine according to the first aspect, wherein the drive mechanism of the tension assisting means comprises a motor and a variable torque clutch, and the driving side of the variable torque clutch is provided. The tension roller is attached to the driven side of the motor, respectively.

A twisting machine according to a third aspect of the present invention is the twisting machine according to the second aspect, characterized in that the drive mechanism of the tension assisting means comprises a variable speed motor and a variable torque clutch.

A twisting machine according to a fourth aspect is the twisting machine according to the first aspect, in which the drive mechanism of the tension assisting means comprises a variable speed motor and a control means, and the control means is the circumference of the tension roller. The rotation speed of the variable speed motor is controlled so that the speed is slightly higher than the traveling speed of the wire.

Further, in the twisting machine according to claim 5, in the twisting machine according to any one of claims 1 to 4, the supply means swings the cradle on which the non-rotating type supply bobbin is mounted and the rotation shaft of the cradle. The present invention is characterized by having a two-twisting type untwisting mechanism provided with a bearing that freely supports and a bow-shaped guide that is attached to the bearing and is provided so as to be rotatable around the cradle.

[0016]

According to the present invention, the twisting machine is driven by the driving mechanism so that the wire tension at the wire inlet portion of the tension roller is equal to or higher than the cumulative tension load on the upstream side of the tension roller and is equal to or lower than the elastic limit value of the wire. As a result, it is possible to prevent the slack and thinness of the strands on the upstream side of the tension roller and the resulting disconnection. Further, since the tension of the strand of the tension roller at the exit of the strand is lower than that of the strand at the entrance by the tension roller, the set tension of the dancer roller can be reduced. Therefore, the strand tension level on the downstream side of the tension roller can be lowered, and the maximum cumulative tension applied to the strand at the inlet of the take-up capstan can be suppressed to the elastic limit value of the strand or less, so that the thinning or There is no risk of disconnection.

In the twisting machine of claim 2, the drive mechanism of the tension assisting means comprises a motor and a variable torque clutch, and the peripheral speed and torque of the tension roller are applied by the motor to the strand by the variable torque clutch. Since the maximum tension can be set freely, it can be easily adjusted to prevent wire breakage and thinning.

In the twisting machine of the third aspect, since the motor is a variable speed motor, it is easy to adjust the peripheral speed of the tension roller.

Further, in the twisting machine according to the fourth aspect, the rotation speed of the variable speed motor is automatically controlled by the control means so that the peripheral speed of the tension roller is slightly higher than the traveling speed of the wire.

Further, in the twisting machine according to the fifth aspect, since the supply means is a double twisting type, the rotation speed for twisting back is only half, which is suitable for high speed.

[0021]

1 is a side view of a twisting machine according to an embodiment of the present invention. 1 is different from the conventional twisting machine of FIG. 6 in that each of the plurality of supply means 10 is provided with a tension assisting device 1. The same means as those of the conventional twisting machine of FIG. 6 are designated by the same reference numerals. 2 is a plan view showing a plurality of supply means 10 and a dancer roller 40 of the stranding machine of FIG. 1, and FIG. 3 is a rear view of the supply means 10, FIG.
FIG. 3 is a plan view showing an example of the tension assisting device 1.

In FIGS. 1 and 2, the tension assisting device 1 is provided on a frame 17 for supporting each supply means 10. As shown in FIG. 3, the supply means 10 includes a supply bobbin 11, a cradle 12 for mounting the supply bobbin 11, a bearing 14 for swingably supporting a rotary shaft 13 of the cradle 12, and a bearing 14 mounted around the cradle 12. And a bow-shaped guide 15 provided so as to rotate. The supply bobbin 11 rotates about its own rotation axis, but the cradle to which it is attached is only swingably supported by the bearing 14 and does not rotate about the rotation axis 13.

In FIG. 4, the tension assisting device 1 comprises a tension roller 2 and a drive mechanism 3 for driving the tension roller 2, and the drive mechanism 3 comprises a motor 4 and a variable torque clutch (hysteresis clutch) 5. is there. A motor 4 is connected to the drive side of the variable torque clutch 5 by a belt 6, and a tension roller 2 is directly connected to the driven side.

A hysteresis clutch, which is an example of the variable torque clutch, will be described below. As shown in FIG. 5, the hysteresis clutch 5 is composed of three parts: a stator 5a, a driving side first rotor 5b, and a driven side second rotor 5c. The stator 5a is an exciting coil 5ar
The first rotor 5b has two inner and outer magnetic poles 5bo and 5b.
i, and a cup-shaped permanent magnet 5cm of the second rotor 5c is inserted between the magnetic poles 5bo and 5bi. When the first rotor is rotated to excite the exciting coil, a rotating magnetic field is generated in the gap 5bg formed between the inner and outer magnetic poles 5bo and 5bi of the first rotor, and the second rotor placed in the gap. The permanent magnet 5cm of 5c is magnetized, but the permanent magnet 5c
m has a hysteresis characteristic, the change in the polarity of the permanent magnet lags behind that of the magnetic pole, and as a result, the first rotor and the second rotor
The rotation of the first rotor is transmitted to the second rotor by magnetically connecting the rotors. That is, the rotation of the drive shaft 5d is transmitted to the driven shaft 5e. And the stator 5a
When the exciting current of the magnetic coil 5ar is made constant, a constant torque can be obtained regardless of the slip rotation speed.

The rotational speed of the motor 4 is set so that the peripheral speed of the tension roller is equal to or higher than the traveling speed of the strand (preferably a speed several% higher than the traveling linear speed) in the state where the variable torque clutch 5 does not slip. Set to. The motor 4 is preferably a variable speed motor in order to facilitate setting of the peripheral speed of the tension roller 2. The set torque (exciting current) of the variable torque clutch 5 is set such that the wire tension at the wire inlet portion of the tension roller 2 is the tension necessary to pull the wire and is equal to or less than the elastic limit value of the wire. To do.

In the variable torque clutch 5, when the torque applied to the tension roller 2 due to the tension of the strand (the torque obtained by adding the torque due to the tension at the inlet of the strand and the torque due to the tension at the outlet) is equal to or more than the set torque, the drive side is driven. Since a slip occurs between 5d and the driven side 5e, there is no risk of excessive tension being applied to the wire. As the variable torque clutch 5, there are a hysteresis clutch, a powder clutch, etc., but the hysteresis clutch is more preferable in consideration of continuous operation and maintenance. When the hysteresis clutch is used, a desired tension can be obtained regardless of the slip rotation speed as described above, so that tension control and speed control are easy.

Further, without using the variable torque clutch 5, a control means for detecting the traveling linear velocity and controlling the rotational speed of the variable speed motor is provided to make the peripheral speed of the tension roller a little faster than the traveling linear velocity. Can also be controlled. In addition, it is easier to control the speed by using the variable torque clutch 5, and the peripheral speed when the wire diameter of the wire changes ((tension roller diameter + wire diameter) × π × tension roller rotation speed) ) Has the advantage that it can be ignored.

Next, the operation of the above twisting machine will be described.
The wire W fed from the supply bobbin 11 is guided by the guide roller R1 and is guided by the guide g provided on the bow-shaped guide 15.
Guided by guide rollers R2, R3, R4, R
It is guided to the dancer roller 40 via the tension roller 2 of the tension assisting means 1 via 5, R16. Then, after being wound around the wheels 41 and 42 for one to two reciprocations, the twisting die 50 is wound through the guide roller 43.
Be led to. Dancer roller 40 and guide roller 4
The three 3 are arranged in the horizontal direction in correspondence with the four supply means 10, and guide the four strands to the dicing die 50. Then, thereafter, by the same means as in the conventional twisting machine, they are twisted and wound.

On the other hand, the twisting by the supply means is given by the rotation of the bow-shaped guide 15. Therefore, in order to increase the manufacturing speed of the twisted wire, it is necessary to increase the rotation speed of the bow guide 15 of the supply means as the rotation speed of the bow guide 33 of the twisting means increases. Therefore, the centrifugal force applied to the wire becomes large, and the frictional resistance between the wire W and the bow-shaped guide 15, the guide roller R1, the guide g ..., The guide rollers R2 ... R5, 16 and the bending resistance of the wire. Is increased, and thus the tension applied to the strand is increased. An increase in frictional resistance due to an increase in centrifugal force due to an increase in speed occurs not only in the contact portion as described above in the supply means but also in all the contact portions up to the pulling capstan 22. The tension T applied generally increases as the tension T applied to the wire W accumulates as it approaches the take-up capstan 22 from the supply bobbin 11.

Therefore, as an example, the tension distribution when four core wires obtained by coating a 0.4 mm annealed copper wire with a polyethylene resin are quad-twisted by the twisting machines of the conventional example and the example will be described. FIG. 7A is a diagram showing a change in tension in the length direction of each core wire when the above-mentioned core wire is quad-twisted by a conventional twisting machine. The solid line shows the tension value in each part when the dancer roller is set so that the maximum tension T _M1 becomes equal to or less than the elastic limit value T _MAX , and the dotted line shows the tension distribution when the set tension of the dancer roller is increased more than that. Show. In the case of the solid line, the load from the supply bobbin to the dancer roller exceeds the set tension of the dancer roller 40, so the winding tension T _M1 by the take-up capstan 22 is distributed over the whole according to the distribution of frictional resistance and the like. A load due to frictional resistance from the supply bobbin to the dancer roller is added to the tension T _S, and the tension value at the dancer roller becomes T _D1 . In this case, since the dancer roller cannot cope with the tension fluctuation, the slack is generated in the wire W passing through the supply means, and the wire is easily entangled and broken. In the case of the dotted line, the tension gradient on the upstream side is increased by increasing the set tension of the dancer roller to T _D2 , and the maximum tension is also that much (T _D2- T _D1 = ΔT)
Increase to T _M2 . In this case, since the highest tension T _M2 exceeds the elastic limit value T _MAX , the strand is thinned.

FIG. 7 (b) is a diagram showing a change in tension when quad twisting is performed by the twisting machine of the embodiment. In this case, the drive mechanism of the tension assisting device causes the wire tension at the wire inlet portion of the tension roller to be equal to or higher than the cumulative tension load on the upstream side of the tension roller and equal to or lower than the elastic limit value of the wire, so that the peripheral speed of the tension roller is low. Since it is driven by the drive mechanism so as to be slightly faster than the traveling speed of the wire, the wire W from the supply bobbin to the tension roller is shown in FIG.
A larger tension is applied to the solid line, and the tension gradient of the line T _S -T _H1 showing the tension distribution is larger than that of T _S -T _D1 . On the other hand, tension T _H2 (T _D3 ) approximately equal to the set tension value of the dancer roller is applied to the strand from the output side of the tension roller to the dancer roller, and the change in tension T _D3 −T _M3 from the dancer roller to the downstream side. Is almost equal to the slope of T _D1 -T _{M1 in} the case of the solid line in FIG. If the set tension value T _D3 of the dancer roller is set equal to that in the case of the solid line, T _M3 also becomes equal to T _M1 and the elastic limit value T _MAX is not exceeded.

In general, as shown in FIG. 8, the relationship between the tension T _H1 on the input side and the tension T _H2 on the output side of the tension roller 2 is obtained by an equation. T _H1 / T _H2 = exp (μθ) where μ: coefficient of friction between the wire and the tension roller θ: contact angle of the wire with the tension roller (2π in the case of one winding) Therefore, for example, the wire W is under tension. 1 to roller 2
When it is wound around and its friction coefficient μ = 0.15, T _H1 / T _H2 = exp (0.15 × 2π) = 2.566. Therefore, the set tension of the dancer roller T _D3 =
If T _H2 is set to 350 g by the weight 43, T _H1 = 8
It becomes 98 g, and the tension of 898 g-350 g = 548 g can be reduced as compared with the case where the tension roller 2 is not provided. Further, when the tension load on the upstream side of the tension roller 2 becomes more than this, it is necessary to further increase the set tension of the dancer roller or to increase the number of times of winding the wire around the tension roller 2.

In the above embodiment, both the twisting means 30 and the twisting back means 15 use bow guides, but such a double twist type is suitable for high speed, and the present invention is applicable to this. The present invention is not limited to this, and can be applied to all twisting machines that have a risk of breaking or thinning due to increased tension load due to high speed. Further, it is preferable from the safety point of view that the drive mechanism of the tension assisting device uses a variable torque clutch, but the drive mechanism is not limited to this. As described above, the traveling linear velocity is detected to control the rotation speed of the variable speed motor. It is also possible to provide a control means and use this control means to synchronize the peripheral speed of the tension roller with the traveling linear speed.

[0034]

According to the twisting machine of the present invention, the wire tension of the wire inlet of the tension roller is equal to or more than the cumulative tension load on the upstream side of the tension roller and the elasticity of the wire is driven by the drive mechanism of the tension assisting device. Since it is driven by the drive mechanism so as to be equal to or less than the limit value, there is no slack in the strand of wire on the upstream side of the tension roller or thinning,
Moreover, disconnection does not occur with them. Further, since the tension of the strand of the tension roller at the exit of the strand is reduced by the tension roller from the tension of the strand at the entrance, the set tension of the dancer roller can be reduced, and the tension of the strand on the downstream side of the tension roller can be reduced. The level of can be lowered. Therefore, the maximum cumulative tension applied to the wire at the inlet of the take-up capstan can be kept below the elastic limit of the wire, and there is no risk of thinning or disconnection. The manufacturing speed of can be increased.

[Brief description of drawings]

FIG. 1 is a side view of an embodiment of the present invention.

FIG. 2 is a plan view of the supply means and dancer roller according to the embodiment of the present invention.

FIG. 3 is a rear view of the supply means of the embodiment of the present invention.

FIG. 4 is a plan view of the tension assisting device according to the embodiment of the present invention.

FIG. 5 is an explanatory diagram of a variable torque clutch according to the embodiment of this invention.

FIG. 6 is a side view of a conventional twisting machine.

FIG. 7 is an explanatory diagram of distribution of tension applied to the wire from the supply bobbin to the take-up capstan.

FIG. 8 is an operation explanatory view of the tension assisting device in the twisting machine of the embodiment of the present invention.

[Explanation of symbols]

1 Tension assisting means 2 Tension roller 3 drive mechanism 4 motor 5 Variable torque clutch 10 Supply means 11 Supply Bobbin 12 cradle 15 Bow-shaped guide (twisting means) 20 Winding means 22 Collection Capstan 30 twisting means 40 Dancer Laura

─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Toshio Sasai 2-3-1, Iwata-cho, Higashi-Osaka City, Osaka Prefecture Tatsuta Electric Wire Co., Ltd. (56) Reference JP-A-61-7511 (JP, A) 51-124124 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) H01B 13/02 B21F 7/00

Claims (5)

(57) [Claims] 1. A plurality of supply means, a twisting means for twisting a plurality of strands supplied from each of the supply means through a dancer roller, and a winding means for winding the twisted strands. In the twisted wire machine, a tension assisting means is provided on the upstream side of the dancer roller in the running path of each strand supplied from the supply means to the twisting means through the dancer roller, and the tension assisting means is configured to It is composed of a tension roller for winding and a drive mechanism for driving the tension roller, and the wire tension at the wire wire inlet portion of the tension roller is equal to or higher than the cumulative tension load on the upstream side of the tension roller and equal to or lower than the elastic limit value of the wire. Driven by the drive mechanism so that the wire tension at the wire exit of the tension roller is lower than the wire tension at the entrance. A twisting machine characterized in that 2. The twisting machine according to claim 1, wherein the drive mechanism of the tension assisting means comprises a motor and a variable torque clutch, wherein the motor is on the drive side of the variable torque clutch and the tension is on the driven side. A twisting machine characterized by being equipped with respective rollers. 3. The twisting machine according to claim 2, wherein the drive mechanism of the tension assisting means comprises a variable speed motor and a variable torque clutch. 4. The twisting machine according to claim 1, wherein the drive mechanism of the tension assisting means comprises a variable speed motor and a control means, and the control means is such that the peripheral speed of the tension roller is lower than the traveling speed of the strand. A twisting machine, characterized in that the rotation speed of the variable speed motor is controlled so as to be slightly faster. 5. The twisting machine according to any one of claims 1 to 4, wherein the supply means includes a cradle to which a non-rotating supply bobbin is mounted, a bearing for swingably supporting a rotation shaft of the cradle, and the bearing. Attached to the cradle and provided with an arc-shaped guide that can rotate around the cradle.
A twisting machine having a twist-twisting mechanism.