JP2002302312A - Take-up controller - Google Patents

Abstract

PROBLEM TO BE SOLVED: To minimize the extension of an operation cycle time while inhibiting the increase of a capacity of a driving device. SOLUTION: The load torque τM required to the driving device in accordance with a rotating speed is calculated by adding the torque for acceleration and deceleration and the torque for tension by an adder 111 during the operation, and the drivable torque corresponding to the rotating speed of the driving device is operated by a rewinding drivable torque operating circuit 113. The rewinding driving load torque τM and the rewinding drivable torque τD are compared by a rewindable torque allowance operating part 112 to calculate the torque allowance, and a speed change rate is determined in accordance with the torque allowance by a speed change rate allowance operating circuit 114 so that the unwinding driving load torque τM is not over the rewinding drivable torque τD at all times.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a winding control device for controlling a winding operation of a winding device.

[0002]

2. Description of the Related Art FIG. 6 is a diagram showing a configuration of a paper winding device. The paper wound on the winding roll 2 is rewound on the rewinding roll 1 while maintaining a predetermined tension T, performs necessary processing, and is wound on the winding roll 2 again. The take-up roll 2 has a rear drum 4, a front drum 5,
It is pressed against each surface of the rider roll 6, and when the rear drum 4, the front drum 5, and the rider roll 6 are respectively driven, the driving force is transmitted to the surface and rotates.

A rewind motor 7 is mounted on the rewind shaft 3 of the rewind roll 1.
The driving force is transmitted by the motor, and the rewinding motor 7
Driven by A driving force is transmitted to the shaft of the rear drum 4 by a rear drum motor 8, and the rear drum motor 7 is driven by a driving device 12. A driving force is transmitted to the shaft of the front drum 9 by a front drum motor 9, and the front drum motor 9 is driven by a driving device 13.

When the paper is taken up by the take-up roll 2, the rewind diameter d of the rewind roll 1 increases as the take-up takes place.
Decrease. Paper tension T and winding speed v (running speed)
Is constant, the rewind roll 1 is reduced with the decrease in the rewind diameter d.
, The load torque required for the driving device 11 decreases.

FIG. 7 is a diagram showing an example of a conventional operation pattern of a paper winding device. In paper winding devices, generally 1
In order to wind up a roll having a plurality of product use dimensions from the rewind roll 1, the operation is such that the acceleration, the constant speed, and the deceleration are repeated as in the operation pattern of the winding speed v shown at the top of the figure. Here, the operation cycle in which the m-th roll is wound is referred to as “m wholesaler (m wholesaler)”. Also,
The winding speed pattern is controlled so that the time integral of the winding speed v becomes a set value so that the winding roll has a standard length. This control will be referred to as “standard-size control”.

In FIG. 7, the lower part of the take-up speed v shows the rewind diameter d, the rewind rotational speed n, and the load of the rewind roll 1 when the take-up speed pattern is the same for each wholesaler. Of the rewinding load torque τ _M and the rewinding drivable torque τ _D of the driving device 11 are shown. As shown in the figure, as the unwinding diameter d decreases, the unwinding rotation speed n increases, and the rewinding load torque τ _M (the absolute value of) decreases every wholesale.

The rewind load torque τ _M becomes maximum during deceleration when the rewind diameter d is the maximum, that is, during deceleration in one wholesaler. This is because, under the same tension, the torque is proportional to the unwinding diameter (see equation (1)), and the deceleration torque is proportional to the inertia moment in the fourth power of the unwinding diameter (formula (1)). 2)) and both act in the same direction.

Τ = T × d / 2 (1) where τ: torque [N · m], T: tension [N], and d: paper roll outer diameter (diameter) [m].

[0009] J = (1/32) × π × L × ρ × (d 4 -D S 4) ... (2) Here, J: inertia moment of the paper roll [kg · ^m 2],
π: Pi, L: Paper width [m], ρ: Paper density [kg / m ³ ],
d: Paper roll outer diameter (diameter) [m], _{D S:} a paper roll inside diameter (diameter) [m].

[0010] Rewindable torque τ of the driving device 11
_D is a characteristic that is greatly reduced in a low-speed rotation range as described below when the AC motor is driven by the inverter.

FIG. 8 is a diagram showing an example of a circuit configuration of the driving device 11. The drive device 11 shown in FIG. 1 converts a DC power supply 20 into an AC variable voltage / variable frequency power supply using an inverter including six-arm semiconductor switches 21a to 21f, and drives the rewind motor 7 as an AC motor at a variable speed. Has become.

Driving device 1 using such an inverter
When a low-frequency output close to DC is output in 1, since only two arms of the six-arm semiconductor switch mainly perform switching operations, heat generation and temperature rise concentrate on these two arms. For this reason, as shown in FIG. 9, the permissible energizing current of the driving device 11 must be reduced in a low frequency region around 0 [Hz] (= DC), that is, in a low speed rotation region. In the figure, I _OL on the vertical axis short overload permissible current, I _N continuous rated current, I _LF is a low-frequency allowable current, F ₁ on the horizontal axis is current, low frequency, F ₂ Is the current low frequency start frequency.

Even in an induction motor widely used for inverter driving, the primary current and the torque have a substantially proportional relationship in a region where the current is large, so that the drivable torque is reduced in the low-speed rotation region as well as the allowable conduction current. Is required.

In actual operation, as shown in FIG. 7, the rewindable torque τ _D (absolute value) of the drive device 11 is reduced to the reduction capability value τ _DLF in the low-speed rotation range. In consideration of this point, it is necessary to apply a drive device having a capacity such that (rewindable drive torque τ _D ) ≧ (rewind load torque τ _M ) in all operation ranges. Note that the rewind driveable torque τ _D and the rewind load torque τ _M
Are compared by absolute values.

FIG. 10 is a diagram for supplementarily explaining the relationship between the rewind rotational speed and the rewind torque due to the change in the rewind diameter.
Here, the range of the base rotational speed N _{B ~} maximum rotational speed N _T during the winding operation, the torque characteristics are, overload rated torque τ
Generally, as shown in _MOL , the output characteristic is constant (torque gradually decreases). This is to effectively use the relationship of the above-described equation (1).

Rewind load torque τ_MBreakdown of mechanical loss
If torque is omitted, acceleration / deceleration torque τ _d(Deceleration torque
Is the acceleration torque) and the tension torque τ_TAlgebraic sum with
You. Tension component torque τ_TIs proportional to the diameter,
Speed torque τ_dIs proportional to the fourth power of the diameter.
And the rewind load torque τ_MIs slower than torque reduction characteristics
The characteristic requires a large load torque in the rotation range. Same figure
Means that the rewind diameter d is between a predetermined value d1 and a minimum value D_SRequired in the range
Satisfies the maximum torque, but in the range of the maximum value dmax to d1
Is an example of insufficient torque.
Causes inconvenience.

For this reason, in the drive device 11, the overload rated torque τ _MOL needs to be equal to or more than the rewind load torque τ _M in the entire operation range, and the reduction capability value τ _{M in the} low speed rotation range is required.
_It was necessary to apply a sufficiently large capacity to the _{rewind driveable} torque τ _D in consideration of _DLF . As described above, the case where the operation is performed with the constant winding speed pattern has been described.

FIG. 11 shows another conventional operation of the paper winding device.
It is a figure showing an example of a pattern. It can be understood in comparison with FIG.
Thus, deceleration in the large range of rewind diameter d (1 wholesale, 2 wholesale)
Set to increase the time, that is, to reduce the speed change rate
The rewind load torque τ _MThe peak value of
You. FIG. 12 shows an example of setting the deceleration time according to the rewind diameter d.
Show. In the range of unwinding diameter dmax to d1 where the driving torque is insufficient
Set a longer deceleration time to avoid torque shortage.
You. As described above, the acceleration / deceleration torque τ _dIs rewind
Since it is proportional to the fourth power of the diameter change, it decreases as the rewind diameter d decreases.
Speed time can be reduced.

[0019]

However, the above-mentioned prior art has the following problems.

[0020] (1) the peak of the rewinding load torque tau _M in the low-speed rotation range of, as shown if Figure 7 that a constant deceleration time in each operating cycle, the winding Modo径d is large range (1 Wholesale) Since the value is large, it is necessary to select a driving device having a capacity such that the drivable torque τ _D is equal to or more than the peak value of the rewinding load torque τ _M even in this low-speed rotation region, and the driving device outer shape becomes large. Along with this, it had to be an expensive system.

(2) Adjusting the deceleration time according to the unwinding diameter d As shown in FIG. 11, by setting the deceleration time to be long in the range where the unwinding diameter d is large, the winding during deceleration can be performed. The peak value of the return load torque τ _M is leveled, and the capacity of the drive device can be reduced as compared with the above (1). However, setting a long deceleration time in advance has a disadvantage that the operation cycle time is increased and the operation rate is significantly reduced.

The present invention has been made in view of the above, and an object of the present invention is to reduce an increase in the capacity of a drive device even when there is a torque reduction characteristic in a low speed rotation range, and An object of the present invention is to provide a winding control device capable of minimizing an increase in operation cycle time.

[0023]

According to a first aspect of the present invention, there is provided a winding control device for rewinding a cylindrically wound material while maintaining a predetermined tension by a driving device. A winding control device that controls a winding operation of the winding device that winds again and then calculates a load torque required for the driving device and a drivable torque of the driving device; Setting means for setting a speed change rate based on the setting.

According to the present invention, a load torque required for the drive unit and a drivable torque corresponding to the rotation speed of the drive unit are calculated according to the operation setting and the operation pattern, and the load torque and the drivable torque are calculated. By setting the speed change rate based on the speed, the speed change rate at the time of acceleration and deceleration is variably controlled according to the rotation speed, so that the most efficient operation pattern is given, and optimum operation can be realized. Like that.

According to a second aspect of the present invention, there is provided a take-up control device for controlling a take-up operation of a take-up device which rewinds a material wound in a columnar shape while maintaining a predetermined tension by a driving device and then rewinds the material. In the winding control device for controlling, a detecting means for detecting a rotation speed of a material, a diameter calculating means for calculating a material diameter, an inertia moment calculating means for calculating a moment of inertia of a material, and the inertia moment and a set speed Acceleration / deceleration torque calculation means for calculating acceleration / deceleration torque based on the rate of change; load torque calculation means for calculating load torque of the drive by adding acceleration / deceleration torque and tension torque; A torque characteristic storage unit for storing in advance the torque characteristics of the driving device with respect to the rotational speed detected by the detection unit and the driving device based on the torque characteristics. Drivable torque calculating means for calculating the drivable torque of the motor, and comparing the load torque calculated by the load torque calculating means with the drivable torque calculated by the drivable torque calculating means, and determining that the load torque indicates the drivable torque. Speed change rate setting means for setting the speed change rate so as not to exceed.

In the present invention, the load torque and the drivable torque are compared, and the speed change rate is set in accordance with the torque margin at this time, so that optimum operation can be realized. ing.

According to a third aspect of the present invention, there is provided the winding control device according to the second aspect, wherein the torque tolerance when the load torque is compared with the drivable torque is determined by comparing the load torque with the drive torque. A torque tolerance storage means for calculating and storing the possible torque as a variable in advance, wherein the speed change rate setting means includes a current value of the load torque calculated by the load torque calculation means, and the drivable torque calculation means The rate of change in speed is calculated based on the current value of the drivable torque calculated by Equation (1) and the torque allowance stored in the torque allowance storage means.

According to the present invention, the torque margin is calculated and stored in advance using the load torque and the drivable torque as variables, and the current values of the load torque and the drivable torque are stored in the memory. By calculating the speed change rate based on the above, optimal operation can be realized with a simpler configuration.

According to a fourth aspect of the present invention, in the winding control apparatus according to the third aspect, a moment of inertia of a material is used as a real time variable of the load torque, and the real time of the drivable torque is adjusted. Is characterized by using the rotation speed of the material as a variable.

According to a fifth aspect of the present invention, in the winding control device according to the third aspect, a material diameter is used as a real time variable of the load torque, and a real time variable of the drivable torque is used. Is characterized by using the rotation speed of the material.

According to a sixth aspect of the present invention, there is provided a winding control device.
Or in the winding control device according to 3, the correspondence relationship between the rotational speed and the material diameter of the material and the speed change rate when the load torque is set so as not to exceed the drivable torque is calculated and stored in advance. The speed change rate setting means includes a rotation speed detected by the detection means, a material diameter calculated by the diameter calculation means, and a speed based on the correspondence stored by the correspondence storage means. It is characterized by obtaining a change rate.

In the present invention, the correspondence between the rotational speed and the material diameter of the material and the rate of change of the speed is calculated and stored in advance, and the current values of the rotational speed and the material diameter of the material and the corresponding values are calculated. Since the speed change rate is immediately obtained based on the relationship, the optimum operation can be realized with a simpler configuration.

According to a seventh aspect of the present invention, in the winding control device according to the sixth aspect, the correspondence storage means stores the initial value in accordance with a tension set value at the time of starting winding. The correspondence is calculated and stored.

According to the present invention, at the start of winding, the correspondence between the rotational speed, the material diameter and the rate of change of the speed is calculated and stored in accordance with the set tension value at that time.
The speed change rate can be obtained with higher accuracy, and optimal operation can be realized.

The winding control device according to the eighth aspect is the second aspect.
8. The winding control device according to any one of claims 1 to 7, wherein the load torque calculating means calculates the load torque by adding the acceleration / deceleration torque, the tension component torque, and the mechanical loss torque.

According to the present invention, by adding a mechanical loss torque (mechanical loss torque) as an element for calculating the load torque, it is possible to obtain the speed change rate with higher accuracy and realize an optimum operation. Can be.

[0037]

Embodiments of the present invention will be described below with reference to the drawings.

[First Embodiment] FIG. 1 is a block diagram showing a configuration of a winding control device according to one embodiment. The winding control device shown in the figure is used for controlling the winding operation of the winding device shown in FIG.

The rewind rotational speed detector 101 detects the rotational speed of the rewind roll 1 by detecting the rotational speed of the drive shaft that transmits power to the rewind shaft 3 that rotates the rewind roll 1.

The take-up rotation speed detector 102 detects the rotation speed of the take-up roll 2 by detecting the rotation speed of a drive shaft for transmitting power to the rear drum 4 and the front drum 5 for rotating the take-up roll 2. .

The winding Modo径calculation circuit 105 compares the output signal of the output signal and the winding rotational speed detector 102 of the rewinding speed detector 101, based on the diameter D _S of the known winding shaft 3 The rewind diameter d of the rewind roll 1 is calculated.

The unwinding moment of inertia calculation circuit 106 calculates the unwinding moment of unwinding of the unwinding roll 1 based on the equation (2) using the unwinding diameter d.

The acceleration / deceleration torque calculation circuit 107 calculates an acceleration / deceleration torque (acceleration torque or deceleration torque) τ _d from the rewind moment of inertia and the acceleration / deceleration rate.

The tension setter (TRH) 108 is for setting the paper tension T. The tension component torque calculation circuit 109 calculates the tension component torque τ _T from the set tension T and the rewind diameter d. Is calculated.

The adder 111 calculates the rewind load torque τ _M by adding the acceleration / deceleration torque τ _d and the tension torque τ _T. The rewinding load torque tau _M is a load torque required according to the operating configuration and operation pattern.

The rewind drivable torque calculation circuit 113 stores the torque characteristic of the drive device 11 in advance because the torque characteristic is known, and based on this torque characteristic and the output signal of the rewind rotational speed detector 101, , A rewind driveable torque τ _D corresponding to the rewind rotation speed is calculated.

The rewind torque allowance calculation circuit 112 compares the rewind load torque τ _M calculated by the adder 111 with the rewind drivable torque τ _D calculated by the rewind drivable torque calculation circuit 113. Thus, a torque margin (torque allowance) corresponding to the rewind rotational speed is calculated.

The shift rate tolerance calculation circuit 114 calculates an appropriate speed change rate (acceleration rate or deceleration rate) according to the torque tolerance, and calculates a speed change rate change command _Rch based on the calculation result as a speed reference calculation. Output to the circuit 104. The calculation of the speed change rate is performed when the torque margin is small, and the rewind load torque τ _M
Determine the deceleration rate so that the peak value is reduced, and when the torque margin is large, define the acceleration rate such that the peak value of the unwinding load torque tau _M increases.

The speed reference calculation circuit (MRH) 104 outputs an acceleration rate (ACC) or a deceleration rate (DEC) based on the speed change rate change command _Rch to the acceleration / deceleration torque calculation circuit 107, and outputs the acceleration rate or the deceleration rate. The setting of the winding speed is changed on the basis of, and the result is output to the fixed length control circuit 103.

The fixed-length control circuit 103 is a control circuit for obtaining a set winding length, and a speed reference arithmetic circuit 104
Speed control is performed according to the winding speed changed in setting. That is, control is performed such that the relationship of (rewind driving load torque τ _M ) <(rewind driving possible torque τ _D ) is ensured in the entire rotation speed range.

Next, a typical operation of the winding control device will be described with reference to FIG. The figure shows an operation pattern of the rewind rotation speed n and the rewind torque τ when the rewind speed (paper traveling speed) is a substantially trapezoidal pattern and the rewind diameter d is large (1 wholesale, 2 wholesale). FIG.

As described above, the rewind driveable torque τ _D is a characteristic that requires a significant reduction in the low-speed rotation range.
The unwinding load torque τ _M is a characteristic that is proportional to the unwinding diameter d and increases during deceleration as compared to during acceleration or at a constant speed.

Here, what is problematic is the A1 part, A
This is a deceleration period in the low-speed rotation region shown in part 2. In the winding control device, even in such a low-speed rotation range, the lengthening of the deceleration time is minimized (rewinding drive load torque τ _M ).
The deceleration rate is set so as to be <(rewindable torque τ _D ), that is, the deceleration time is set to be long.

In the part A1 of FIG._d1In
Low speed range t _d2Deceleration rate at
Shows a state when is set low. This allows for low speed
Rotation range t_d2Deceleration time is longer by the minimum required
And the rewinding drive load torque τ_MCan be driven to rewind the peak value of
Torque τ_DTo a value not exceeding.

Therefore, according to the present embodiment, during operation, the rewind drive load torque τ _M and the rewind drive enable torque τ _D are calculated, and the rewind drive load torque τ _M is calculated as the rewind drive enable torque τ _D. The speed change rate is set so that it does not exceed the maximum speed, so the speed change rate during acceleration and deceleration is variably controlled according to the rotation speed, so that the most efficient operation pattern is given and optimal operation is performed. Therefore, the increase in the operation cycle time can be minimized while suppressing the increase in the capacity of the drive device. In addition, thereby, the rated capacity of the drive device can be significantly reduced.

[Second Embodiment] The feature of the second embodiment is that the rewinding load torque τ _M and the rewinding drivable torque τ _D are real-time variables, and the driving when the tension is known. The torque tolerance of the apparatus or the speed change rate to be set is calculated and stored in advance, and the torque tolerance and the speed change rate can be immediately obtained by giving a variable during operation. The basic configuration of the winding control device according to the present embodiment is the same as that of FIG. 1 and the operation pattern is also the same as that of FIG.

As described above, the rewind load torque τ _M
Since is calculated using a winding moment of inertia, it is possible to use the moment of inertia as a real-time variable rewinding load torque tau _M. The moment of inertia because it is calculated using the winding Modo径d, it is also possible to use a winding Modo径d as a real-time variable rewinding load torque tau _M. On the other hand, the rewind rotational speed n can be used as a real-time variable of the drivable torque τ _D.

The tension is assumed to be the maximum value in the specification, the rewind load torque τ _M is set so as not to exceed the drivable torque τ _D , and the rewind diameter d and the rewind rotational speed n are given. It is also possible to calculate in advance the speed change rate to be set at the time of off-line, and store the correspondence between the rewind diameter d and the rewind rotation speed n and the speed change rate. In this case, during operation, the rewind diameter d and the rewind rotational speed n
Is used as a variable, and the speed change rate can be immediately obtained based on the above correspondence.

FIG. 3 shows an example of this operation setting. FIG. 11 is a graph showing the correspondence between the rewind diameter d, the rewind rotational speed n, and the deceleration time. In the figure, the deceleration time on the vertical axis using the t _d speed variation rate is to be obtained indirectly. Deceleration time t _d is the function curved surface S _R in which the winding Modo径d and rewinding speed n as a variable.

Note that the vicinity of t _d ′ on the axis of the deceleration time t _d is the low-speed rotation region, and the vicinity of t _d ”is the high-speed rotation region.
The D _s on the axis rewind shaft diameter, boundary value when d ₁ is the speed change ratio varies largely, d _max is the winding Modo径maximum value.

Therefore, according to the present embodiment, the winding control device can be realized with a very simple configuration.

When the operation is started, an appropriate speed change rate is automatically calculated in accordance with the tension set value at that time, and the speed reference calculation (MRH) circuit 104 is controlled. Can be controlled.

[Third Embodiment] FIG. 4 is a block diagram showing a configuration of a winding control device according to the present embodiment. This embodiment is different from the above embodiments in that a mechanical loss torque (mechanical loss torque) is considered.

In this figure, a mechanical loss torque setting device 110 is newly provided in FIG. 1, and an adder 115 adds the mechanical loss torque, the acceleration / deceleration torque, and the tension torque to obtain a rewind load torque. τ _M is obtained. As a result, a more accurate speed change rate can be calculated.

[Application to Other Embodiments] The first,
Although the second and third embodiments have been described, the present invention can be simplified by using the winding speed V instead of the rewind rotation speed n in common to all the embodiments. In this case, the speed change rate change point may be set by associating the rewind rotation speed n and the winding speed V when the rewind diameter is large. Rewind diameter d
, The speed change rate reduction range becomes slightly longer than necessary, and the operation cycle time is slightly extended.
However, in practice, this method can provide a great effect over the prior art.

In each of the above embodiments, the case where a paper winding device is used as an example has been described. However, the present invention can be similarly applied to other winding devices such as an iron coil. FIG. 5 is a diagram illustrating an example of a mechanical configuration of the temper rolling device. This figure shows speed control using the rolling rolls 53 and 54 as a speed master. The rewinding machine generates torque in the braking direction by the electric motor 57, and the winding machine generates torque in the pulling direction by the electric motor 58. Each is operated under tension (torque) control.

For a rewinding machine, the application of this method is effective in a low speed region immediately before deceleration stop in a range where the rewinding diameter is large, and for a rewinding machine when the winding diameter is large. The application of this method is effective in the low-speed region at the start of acceleration, and the rated capacity of the driving device can be greatly reduced.

In the above embodiments, the speed change rate is changed according to the torque margin. However, the speed change rate becomes substantially constant in order to suppress the tension change at the speed inflection point. By performing such "rounding" based on the speed, and by setting this rounding to a large value, the load torque required in the low-speed rotation region is reduced, and the same effect can be obtained. In the case of rounding, in order to reduce the influence on the operation cycle time, rounding only in the low-speed rotation range during deceleration is large for rewinding machines, and only for low-speed rotation range during acceleration for winding-up machines. Should be set large.

In each of the above embodiments, the case where an inverter is used as a drive device for driving an AC motor has been described as an example. However, the present invention is not limited to an inverter.
When a drive device whose torque characteristics change according to the rotation speed is used, by setting the speed change rate according to the rotation speed in the same manner as described above, it is possible to realize operation control that optimizes the capacity of the drive device. it can.

For example, when a DC separately excited motor is driven by a Leonard device, if the constant output range (field control range) is widened, the rectification state becomes worse due to the armature reaction as the field is weakened. Restrictions may need to occur. In such a case, the capacity of the driving device can be optimized by reducing the speed change rate in a region where the field weakening amount is large, that is, in a region where the rotation speed is high.

[0071]

As described above, according to the winding control device according to the present invention, the load torque and the drivable torque of the drive device are calculated, and the speed change rate is calculated based on the load torque and the drivable torque. By setting, the rate of change in speed during acceleration and deceleration is variably controlled in accordance with the rotation speed, so that the most efficient operation pattern is given and optimal operation can be realized, and thus the capacity of the drive unit is reduced. It is possible to minimize the increase in the operation cycle time while suppressing the increase. In addition, thereby, the rated capacity of the drive device can be significantly reduced.

[Brief description of the drawings]

FIG. 1 is a block diagram illustrating a configuration of a winding control device according to a first embodiment.

FIG. 2 is a diagram showing an operation pattern of a rewind rotation speed and a rewind torque.

FIG. 3 is a diagram illustrating a function surface of a deceleration time with a rewind diameter and a rewind rotational speed as variables.

FIG. 4 is a block diagram illustrating a configuration of a winding control device according to a third embodiment.

FIG. 5 is a diagram showing an example of a mechanical configuration of a temper rolling device.

FIG. 6 is a diagram illustrating a configuration of a paper winding device.

FIG. 7 is a diagram showing an example of a conventional operation pattern of a paper winding device.

FIG. 8 is a diagram illustrating an example of a circuit configuration of a drive device that drives the rewind motor.

FIG. 9 is a diagram illustrating a frequency characteristic of a permissible energizing current of the driving device.

FIG. 10 is a diagram for supplementarily explaining a relationship between a rewind rotation speed and a rewind torque due to a change in rewind diameter.

FIG. 11 is a diagram showing an example of another conventional operation pattern of a paper winding device.

FIG. 12 is a diagram showing an example of setting a deceleration time according to a rewind diameter.

[Explanation of symbols]

 Reference Signs List 1 rewind roll 2 take-up roll 3 rewind shaft 4 rear drum 5 front drum 6 rider roll 7 rewind motor 8 rear drum motor 9 front drum motor 11, 12, 13 drive device 20 DC power supply 21a, 21b, 21c semiconductor switch 21d, 21e, 21f Semiconductor switch 101 Rewind rotation speed detector 102 Rewind rotation speed detector 103 Standard length control circuit 104 Speed reference calculation circuit 105 Rewind diameter calculation circuit 106 Rewind inertia calculation circuit 107 Acceleration / deceleration torque calculation circuit 108 Tension Setting device 109 Tension component torque calculation circuit 110 Mechanical loss torque setting device 111 Adder 112 Rewind torque tolerance calculation circuit 113 Rewind driveable torque calculation circuit 114 Gear ratio tolerance calculation circuit 115 Adder

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Hiroyuki Yuasa 3-13-16 Mita, Minato-ku, Tokyo Inside Toshiba GE Automation Systems Corporation (72) Inventor Nobuyuki Iizuka 3-13- Mita, Minato-ku, Tokyo 16 F-term (reference) 3F105 AA01 AB15 BA02 BA08 BA22 CA02 CA06 CA13 CB02 CC01 CC02 CC03 CC04 CC08 DA05 DA12 DA15 DA17 DA23 DA45 DB05

Claims (8)

[Claims] 1. A winding control device for controlling a winding operation of a winding device that rewinds a material wound in a columnar shape while maintaining a predetermined tension by a driving device and then rewinds the material. And a setting means for setting a speed change rate based on the load torque and the drivable torque, and a winding control device. 2. A winding control device for controlling a winding operation of a winding device which rewinds a cylindrically wound material while maintaining a predetermined tension by a driving device and then rewinds the material. Detecting means for detecting; diameter calculating means for calculating the material diameter; inertial moment calculating means for calculating the moment of inertia of the material; and accelerometer for calculating the acceleration / deceleration torque based on the inertia moment and the set speed change rate. Deceleration torque calculation means, load torque calculation means for calculating the load torque of the drive by adding the acceleration / deceleration torque and the tension torque, and a torque in which torque characteristics of the drive with respect to the rotation speed are stored in advance. A characteristic storage unit, and a drivable unit that calculates a drivable torque of the driving device based on the rotation speed detected by the detection unit and the torque characteristic. A torque calculating means, comparing the load torque calculated by the load torque calculating means with the drivable torque calculated by the drivable torque calculating means, and setting a speed change rate such that the load torque does not exceed the drivable torque. And a speed change rate setting means. 3. A torque margin storage means for calculating and storing in advance a torque margin when comparing the load torque with the drivable torque using the load torque and the drivable torque as variables, and The rate setting means includes a current value of the load torque calculated by the load torque calculation means, a current value of the drivable torque calculated by the drivable torque calculation means,
3. The winding control device according to claim 2, wherein a speed change rate is calculated based on the torque allowance stored in the torque allowance storage means. 4. The winding control device according to claim 3, wherein a moment of inertia of the material is used as a real-time variable of the load torque, and a rotation speed of the material is used as a real-time variable of the drivable torque. 5. The winding control device according to claim 3, wherein a material diameter is used as a real-time variable of the load torque, and a rotation speed of the material is used as a real-time variable of the drivable torque. 6. A correspondence storage means for calculating and storing in advance the correspondence between the rotational speed and the material diameter of the material and the speed change rate when the load torque is set so as not to exceed the drivable torque. The speed change rate setting means obtains a speed change rate based on the rotation speed detected by the detection means, the material diameter calculated by the diameter calculation means, and the correspondence stored by the correspondence storage means. The winding control device according to any one of claims 2 to 5, wherein 7. The winding control device according to claim 6, wherein the correspondence relation storage means calculates and stores the correspondence relation according to a tension set value at that time when winding is started. 8. The load torque calculating unit according to claim 2, wherein the load torque calculating unit calculates the load torque by adding the acceleration / deceleration torque, the tension component torque, and the mechanical loss torque. Winding control device.