KR20010059955A - Apparatus for regulating wire tension for wire twister - Google Patents

Abstract

PURPOSE: A tension controller is provided to minimize a change of quality by automatically controlling braking force according to weight of a bobbin and uniformly maintaining tension of supplied wires. CONSTITUTION: A tension controller(20) comprises a bobbin for supplying a wire(10); a first and a second guides(21,22) to guide the wire(23) from the bobbin(10) by installing outside the bobbin(10); a dancer body(24) elastically installed in the opposite side to the guides(21,22); and a band brake lining(25) contacted with a flange of the bobbin(10) by fixing in the dancer body(24). Many wires are arranged between the second guide(22) and a guide boom(24a) and moved by reciprocating between the guide(22) and the guide boom(24a).

Description

Wire tension tensioning device for stranded wires {Apparatus for regulating wire tension for wire twister}

The present invention relates to a twisted pair for steel cord manufacturing used as a reinforcement material for rubber products such as tires and conveyor belts of automobiles, and more specifically, a wire tensioning dancer installed in an outer side of a steel cord winding bobbin has a multi-wire type, It is a structure consisting of a brake system that combines a band brake lining made of a material with low friction coefficient, so that the tension of the wire supplied according to the size of the bobbin is always equalized during full winding and burnout, thereby minimizing the quality change of the wire. It is related to the tensioning device of the supply line of the twisted pair.

In general, among the various types of reinforcing materials used for reinforcing rubber products such as tires and conveyor belts of vehicles, steel cords are superior to other rubber reinforcing materials in terms of strength, modulus, heat resistance, and fatigue resistance. It is known to exhibit excellent properties, thereby greatly contributing to the improvement of wear resistance, durability and adjustment stability, especially when used in carcass or belt layers as tire reinforcement.

Recently, due to the high strength of the steel cord according to the trend of lighter weight of the tire has a sensitive effect on the quality of the steel cord due to the tension change of the wire, and the use of the multi-stage winding machine to increase the operating time of the twisted pair, so The trend is to increase the size of bobbins by avoiding any changes in strand tension.

Particularly, in the case of steel cord manufacturing machines, the conversion from general-purpose machine capable of producing steel cords with various structures to dedicated twisted-pair machine manufactured to produce only specific structures professionally is possible. Specialization must be preceded by the development of additional systems to produce high quality wire products compared to small bobbins.

This is to simplify the auxiliary devices to be able to manufacture high quality steel cord products at the same time as the high-speed work in accordance with the structural characteristics of the large and specialized bobbin.

In general, since the bobbin used in the conventional twisted pair is small, it is configured to wire the dancers in a single wire to adjust the tension of the wires supplied from the bobbin. It is not possible to adjust the tension evenly.

In addition, when a large bobbin is used in a conventional stranded structure, the moment of inertia is severely changed due to the weight difference of the bobbin wound on the bobbin, and thus, different braking force must be applied at the time of full winding and burnout, that is, in case of full winding bobbin. As the moment is increased, the braking force must be large to adjust the tension, and the moment of inertia due to the weight reduction of the bobbin decreases toward the bobbin, so the braking force must be gradually reduced.

However, the conventional twisted pair has been pointed out that it is difficult to apply a braking device for a large bobbin because it always controls the rotation of the bobbin with only a constant braking force.

Accordingly, the present invention has been made in order to solve the above-mentioned disadvantages and problems that are pointed out in the conventional twisted pair structure, the wire is multi-wired on the guide rod of the dancer body to make the interlocking action with the guide roller installed on the outside of the bobbin The structure consists of a brake system that combines a band brake lining with a low friction coefficient material and a chain, so that the braking force can be automatically adjusted according to the weight of the bobbin when the bobbin is full and exhausted. An object of the present invention is to provide a supply wire tension control device for a twisted pair of wires by minimizing the quality change of the wire wire by keeping the tension constant.

1 is a cross-sectional view of a bobbin BA-80 used in the apparatus of the present invention.

2 and 3 are views of the element wire supply structure of the bobbin of the present invention,

Figure 2 is a front view of the supply line tension control device of the twisted pair of the present invention.

3 is a schematic side view of FIG.

((Description of the code for the main part of the drawing))

10. Bobbin 21,22. Guide roller

23. Wires 24. Dancer's body

24a. Guide rod 25. Brake lining

25a. Teflon resin 25b. chain

The object of the present invention is a dancer body in which wires are multi-wired to guide rods to adjust the tension of the wires supplied to the chain brake lining of the structure coupled with the low friction coefficient Teflon material and the chains on the outer circumferential surface of the bobbin. It is achieved by the structure made up.

The wire tension adjusting device of the twisted pair of the present invention controls the braking force applied to the bobbin by combining the dancers and the chain brake linings in which the wires are multi-wired, and the tension change of the wires due to the weight difference when the bobbin is full and exhausted. There is a technical feature to minimize the change in the quality of the wire by making almost no.

The type of bobbin used in the twisted pair structure of the present invention is the BA-80 bobbin, the largest bobbin used in steel cord twisted pair, and serves as a main component of a brake system for controlling tension of element wires in the twisted pair structure described below. do.

Details of the technical configuration and the effects according to the above object of the present invention will be clearly understood by the following detailed description based on the drawings showing preferred embodiments of the present invention.

First, Fig. 1 is a cross-sectional view of a bobbin BA-80 used in the apparatus of the present invention, in which a wire 12 is wound with a constant thickness on the core barrel 11 of the bobbin 10 as shown. It consists of a structure.

The bobbin used in the present invention (BA-80) is composed of a standard product is manufactured in the dimensions shown in Figure 1, when the moment of inertia (J) according to the weight change of the bobbin is shown in Table 1 below.

In general, the weight W is obtained by multiplying the specific weight of the material by the volume of each component calculated in the drawing.

<< Calculation of moment of inertia of BA-80 bobbin >> Item Ten thousand Sojin Weight (W) ①π / 4 × (33 ² -5.6 ² ) × 1.8 × 7.8 / 1000 × 2 = 23.32 kg ②π / 4 × {(30.5 ² -12.5 ² ) × 0.827 + (12.5 ² -5.6 ² )} × 2.2 × 7.8 / 1000 × 2 = 20.62 ㎏③π / 4 × (30.5 ² -12.5 ² ) × 0.827 × 15.6 × 7.8 / 1000 + 5.375 = 66.55 ㎏① + ② + ③: 23.32 + 20.62 + 66.55 = 110.49 ㎏ (Wire weight: 78.4 ㎏ ) ①π / 4 × (33 ² -5.6 ² ) × 1.8 × 7.8 / 1000 × 2 = 23.32 kg ②π / 4 × (12.5 ² -5.6 ² ) × 2.2 × 7.8 / 1000 × 2 = 3.366 kg③π / 4 × (12.5 ² -10 ² ) × 15.6 × 7.8 / 1000 = 5.375 kg① + ② + ③: 23.32 + 11.66 + 3.366 = 32.06 kg Weight Second Moment (I) ^{I = 1 / 2W (R 2} - r 2) ㎏ · ㎠①1 / 2 × 23.2 (16.5 2 - 2.8 2) = 3083 ㎏ · ㎠②1 / 2 × 20.6 (15.25 2 - 2.8 2) = 2478.5 ㎏ · ㎠③1 ^{/ 2 × 66.6 (15.25 2 -} 6.25 2) = 9038.3 ㎏ · ㎠① + ② + ③ = 14600 ㎏ · ㎠ ^{I = 1 / 2W (R 2} - r 2) ㎏ · ㎠①1 / 2 × 23.2 (16.5 2 - 2.8 2) = 3083 ㎏ · ㎠②1 / 2 × 3.37 (6.25 2 - 2.8 2) = 79 ㎏ · ㎠③1 ^{/ 2 × 32.06 (6.25 2 -} 10 2) = 9038.3 ㎏ · ㎠① + ② + ③ = 4189 ㎏ · ㎠ Moment of Inertia (J) G = I / g = 14600/980 = 14.90 ㎏ cm ² sec ² G = I / g = 14600/980 = 4.27 ㎏ cm ² sec ²

As shown in Table 1, it can be seen that the difference in moment of inertia (J) of about three times occurs when the bobbin wire is wound up and exhausted.

Next, Figures 2 and 3 are views of the element wire supply structure of the bobbin of the present invention, Figure 2 is a front view of the supply line tension control device of the twisted pair of the present invention, Figure 3 is a schematic side view of FIG.

As shown, the supply wire tension control device 20 of the twisted pair of the present invention is installed at regular intervals on the outside of the bobbin supply bobbin 10 and the bobbin 10 is drawn out from the bobbin 10 First and second guides 21 and 22 for guiding the outgoing element wires 23, the dancer body 24 elastically installed on the opposite side of the first and second guides 21 and 22, and one end portion It is composed of a chain brake lining 25 which is fixed to the dancer body 24 in contact with the flange outer side of the bobbin 20, wherein the element wire 23 via the first guide 21 is a second guide Multiple wires between the 22 and the guide rod 24a coupled to the end of the dancer body 24 are configured to move while reciprocating between these two members 22 and 24a several times.

The element wire 23 supplied from the bobbin 10 is guided by the guide rollers 21 and 22 to be configured to be at least three times in a zigzag form on the guide rods 24a of the dancer body 24. ), The element wire 23 is multi-wired.

In addition, on the flange outer circumferential surface of the bobbin 10 so that the chain brake lining 25, one end of which is fixed to the dancer body 24 is wound so that the tension is applied in accordance with the flow of the dancer body 24, the rotation speed of the bobbin It is configured to adjust.

On the other hand, the chain brake lining 25 is fixed on a spring provided on one side end of the dancer body 24 and the other end is connected to a predetermined fastener 27 is bobbin (according to the constant flow of the dancer body 24) 10) It is configured to adjust the tension applied to the outer peripheral surface of the flange, Teflon-based resin 25a having a low coefficient of friction to the inner surface and the outer surface of the chain to facilitate the transfer of force in accordance with the rotation of the dancer 24 The structure 25b combines.

The symbol shown in FIG. 2 indicates various acting forces applied to the tension equalization device 20 of the present invention, and calculates torques, braking force, repulsive force, tensile force, etc. applied to the present invention, and calculates the calculated values and actual values. In comparison,

First, the equilibrium equation of the force of the supply line tension control device 20 of the present twisted pair

Where Fs is the repulsive force of the dancer spring,

T ₂ : tensile force of the brake band,

Fw: Dancer action of element tension.

Next, when the torque (Tb) acting on the bobbin 10 at the time of full winding and burnout of the element wire 12 is obtained,

Tb = Tm + Tw

Where Tm is the torque due to the moment of inertia of the bobbin

Tw: Torque by small wire tension

α: angular acceleration,

The moment of inertia of the bobbin 10 is greatest when full winding, and the braking time of the bobbin during sudden stop should be able to absorb the loose part of the wire caused by the bobbin's jungle at least at the dancer. Assume that the braking time t is calculated as follows.

The braking time (t) is the value obtained by dividing the relaxation length by the speed of the ship. The relaxation distance is 6 × 30 = 180 mm because the three-wire dancer is used. The speed of the ship (V) is 4000 RPM × 18/60 = 1200 mm / sec. Then, braking time (t) is calculated as 0.25 sec by 180/1200.

In addition, the angular acceleration α is defined by the following equation,

Where ω: angular velocity (2πN / 60 rad / sec ² )

N: Bobbin Rotation Speed

Full volume N = 72000 / (305 × π) = 75.1 rpm

The calculated result is 52.4 rad / sec ² .

The torque Tm by the moment of inertia of the bobbin is 780 kg · m when substituted into the formula (I / g) × α.

In addition, the dancer action force (Fw) of the element wire tension is expressed as the product of the element wire tension and the element winding radius, and the result is calculated as 45.75 ㎏ · m. Tb) is 781 + 45.75 = 826.1 kgm.

In this way, when the torque Tb acting on the depleted bobbin is removed, the torque Tb at exhaustion is 565.9 kg · m, and the braking torque Tb for maintaining the tension of the wire is at It can be seen that it is approximately 1.5 times larger than the bobbin.

Next, the following equation is used to find the tensile force (T ₂ ) of the single-acting band brake.

Where μ: coefficient of friction (Teflon series: 0.075)

θ: contact angle (180 ° = πrad)

f: Brake braking force (kg).

At this time, when the brake braking force applied to the above formula is obtained, the braking force (f) is calculated by substituting the formulas of Tb × 2 / Db (Db: diameter of the brake wheel: 198 mm) for full winding and exhausting, respectively. After the braking force (f) of 83.5kg and 57.2kg is calculated, it is designed into 393kg and 269.5kg by substituting the equation ( ₄ ) to calculate the single-acting brake tension (T ₂ ).

However, since the maximum braking force is required at the full winding of the element wire, the tensile force T ₂ applied to the brake band based on the full bobbin winding is applied at 393 kg.

Next, when calculating the repulsive force of the dancer spring, if Binary shift L ₁ to the left side in Equation 1, Fw = (T ₂ L ₂ + FwL ₃ ) / L ₁ , where L ₁ = 70 mm, L ₂ = 50 Mm, L ₃ = 165 mm and Fw is the element tension which acts on a dancer, and when it substitutes 6xt = 18 kg, Fs calculates 323 kg.

At this time, the Fw can be seen that the force acting on the dancer is six times by wiring three guide rollers, the repulsive force of the spring is required to 323 kg.

In contrast to the theoretical value calculated as described above, the test results are substituted into the measured values of the actual specifications of the twisted pair of the present invention.

First, the load Fs of the spring is calculated by the following equation.

Where δ: displacement of the spring (5 mm)

G: modulus of elasticity (7.5 × 10 ³ ㎏ / ㎠)

D: Effective diameter of spring (8.5mm)

d: spring wire diameter (4.5mm)

N: Effective turns of spring (10)

When the values are substituted and calculated, 313 kg is obtained.

At this time, the actual wire tension of the bobbin is shown in Table 2.

Dancer springs Winding tension (g) Length (mm) Displacement (mm) All rights When exhausted 65 5 2900 67 3 3000

Based on Table 2, the torque Tb is calculated to calculate the actual braking force and the tensile force. The equation 2 is used to calculate 825.3 kg · cm at full volume and 565.7 kg · cm at exhaustion, and the braking force f is 10,000. 83.4 kg per hour and 57.2 kg for exhaustion.

The braking force (f) is based to exhibit the actual tensile force (T ₂₎ to run out when 269.5 ㎏ and 392 ㎏ when million volumes look determined by the equation (4) for Again a tensile force at the time of million volumes as in the theoretical value (T ₂₎ It would be desirable to select.

Next, when the repulsive force (Fs) of the dancer spring and the load (W) according to the spring displacement amount are sequentially calculated by the above equations (1) and (5), the repulsive force (Fs) of the dancer spring is 17.4 kg at all windings and is exhausted. It is 18 kg, and the load (W) according to the spring displacement amount is calculated to be 313 kg in full winding and 187.8 kg in exhaustion.

As such, the calculated theoretical value and the actual calculated value show a difference between the difference of 7 kg in full volume and 3 kg in exhaustion, so that the calculated value and the measured value calculated when the actual machine is operated are almost similar. .

As described above, the supply wire tension control device of the twisted pair of the present invention is the instantaneous tension change of the wire is supplied as a structure in which the wire is multi-wired to the guide rod of the tension control dancer installed on the outer wire movement path of the bobbin In addition to being able to absorb the and has the advantage of being able to exhibit a large braking force with a small force because it is configured in the form of a guide roller and pulley type.

In addition, the supply line tension adjustment device of the twisted pair of the present invention is a friction surface by forming a combination of a brake lining material that is installed to contact on the outer peripheral surface of the rotating bobbin flange and a chain of Teflon resin having a low friction coefficient By improving the contact efficiency of, there is an advantage that the tension of the wire can be changed immediately according to the change of the position of the dancer.

Due to the advantages described above, a stable element tension can be maintained by enabling the absorber to absorb the momentary shortage or excess element length during start and stop of the twisted pair.

Claims (2)

First and second guides 21 and 22 for guiding element wires 23 and the element wires 23 drawn out from the bobbin 10 at regular intervals on the outside of the bobbin 10. And the dancer body 24 elastically installed on the opposite side of the first and second guides 21 and 22 and the flange body of the bobbin 20 with one end fixed to the dancer body 24. It is composed of a chain brake lining (25), wherein the element wire 23 via the first guide 21 is between the second guide 22 and the guide rod 24a coupled to the end of the dancer body (24) Supply line tension control device for a twisted pair, characterized in that the multiple wires to be configured to move while reciprocating between these two members (22, 24a) several times. The apparatus of claim 1, wherein the guide rod (24a) is such that the element wire (23) supplied from the bobbin (10) is made of at least three wires.