Roll press device and control device

Abstract

Provided is a roll press device wherein a thickness gauge is provided to the output side of a first pressure roller and a second pressure roller, and detects the thickness of a secondary battery electrode plate at each of three or more points in the width direction of said electrode plate. From the measured thickness values at the three or more points and a target thickness value, a calculation unit: calculates three feature values comprising a first deviation between the target thickness value and the measured thickness value at the point among the three or more points that is closest to a first compressing mechanism, a second deviation between the target thickness value and the measured thickness value at the point among the three or more points that is closest to a second compressing mechanism, and a secondary component of the thickness profile of the electrode plate; and adaptively changes the set values of the first compressing mechanism, the second compressing mechanism, a first bending mechanism, and a second bending mechanism on the basis of the three feature values.

Description

[Technical field]

[0001] The present disclosure relates to a roll press device that rolls electrode plates of secondary batteries, and a control device. [Background technology]

[0002] In recent years, shipments of secondary batteries have been increasing with the spread of electric vehicles (EVs), hybrid vehicles (HVs), and plug-in hybrid vehicles (PHVs). In particular, shipments of lithium-ion secondary batteries have been increasing. A typical secondary battery mainly comprises a positive electrode, a negative electrode, a separator, and an electrolyte. A roll press device is used in the compression processing step, which is one of the steps in manufacturing positive and negative electrode plates for secondary batteries (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2013-111647 A Summary of the Invention

[0004] In the compression processing process of electrode plates in a roll press device, a thickness accuracy of about 2 μm or less is generally required. The thickness of the electrode plate changes in the length and width directions during compression processing due to changes in the coating thickness of the electrode material in the previous process, or changes in the roll outer diameter due to processing heat and bearing heat generated during the compression process. If the thickness exceeds the control range, the line must be stopped and the press conditions must be manually reset to adjust it within the control range, and the thickness parts that cannot be applied to the product must be removed, resulting in a decrease in facility operation rate and a decrease in yield.

[0005] In recent years, there has been an increasing demand for secondary batteries to be small, lightweight, and have high capacity, or to have high capacity while maintaining the same manufacturing cost. In battery design, the length of the electrodes is determined so that they can fit into the battery case, whether cylindrical or rectangular. Even if the electrode length is the same, if the thickness is large, the winding diameter when the electrode is wound will be large. Therefore, the length of the electrode is determined taking into account the range of thickness variations that occur during manufacturing. In other words, if the thickness precision can be increased, the length of the electrode can be increased, making it possible to design batteries with higher capacity.

[0006] In order to solve the above problems, a roll press device according to one aspect of the present disclosure includes a first pressure roller and a second pressure roller that sandwich and roll electrode plates of secondary batteries that are continuously transported, a first main bearing portion and a second main bearing portion that are provided on one side and the other side of a rotation shaft of the first pressure roller, respectively, and rotatably support the rotation shaft, a third main bearing portion and a fourth main bearing portion that are provided on one side and the other side of the rotation shaft of the second pressure roller, respectively, and rotatably support the rotation shaft, a first bend bearing portion and a second bend bearing portion provided on one side and the other side of the rotation shaft of the second pressure roller, respectively, and rotatably supporting the rotation shaft; a third bend bearing portion and a fourth bend bearing portion provided on one side and the other side of the rotation shaft of the second pressure roller, respectively, and rotatably supporting the rotation shaft; a first compression mechanism capable of applying a load to at least one of the first main bearing portion and the third main bearing portion in a direction in which the first pressure roller and the second pressure roller approach each other; the first pressure roller and the second pressure roller are provided with a second compression mechanism capable of applying a load in a direction in which the first pressure roller and the second pressure roller approach each other; a first bend mechanism capable of applying a load to at least one of the first bend bearing portion and the third bend bearing portion in a direction in which the first pressure roller and the second pressure roller separate from each other; a second bend mechanism capable of applying a load to at least one of the second bend bearing portion and the fourth bend bearing portion in a direction in which the first pressure roller and the second pressure roller separate from each other; a thickness gauge provided on the exit side of the first pressure roller and the second pressure roller, the thickness gauge detecting a thickness of an electrode plate of the secondary battery at three or more points in a width direction of the electrode plate; a calculation unit calculating setting values ​​of the first compression mechanism, the second compression mechanism, the first bend mechanism, and the second bend mechanism based on the three or more thickness measurement values ​​based on the detection values ​​of the thickness gauge and a target thickness value; and a control unit controlling the loads of the first compression mechanism, the second compression mechanism, the first bend mechanism, and the second bend mechanism based on the setting values ​​calculated by the calculation unit.The calculation unit calculates three feature amounts: a first deviation between the target thickness value and the thickness measurement value of the point among the three or more points that is closest to the first compression mechanism, a second deviation between the target thickness value and the thickness measurement value of the point among the three or more points that is closest to the second compression mechanism, and a second component of the thickness profile of the electrode plate, and adaptively changes setting values ​​of the first compression mechanism, the second compression mechanism, the first bend mechanism, and the second bend mechanism based on the three feature amounts.

[0007] According to the present disclosure, it is possible to achieve high-precision thickness control of a roll press device. [Brief description of the drawings]

[0008] [Figure 1] FIG. 1 is a schematic front view of the roll press device according to the first embodiment. [Diagram 2] FIG. 2 is a schematic front view of the roll press device according to the second embodiment. [Diagram 3] FIG. 3 is a schematic front view of the roll press device according to the third embodiment. [Figure 4] FIG. 4 is a schematic side view of the roll press devices according to the first to third embodiments. [Diagram 5] FIG. 5 is a diagram for explaining a feedback control example 1 using the first control panel and the second control panel. [Figure 6] FIG. 6 is a diagram for explaining a feedback control example 2 using the first control panel and the second control panel. [Figure 7] FIG. 7 is a diagram for explaining a feedback control example 3 using the first control panel and the second control panel. [Figure 8] FIG. 8 is a diagram for explaining a fourth feedback control example using the first control panel and the second control panel. [Figure 9] FIG. 9 is a plot of the relationship between the change in thickness of the electrode plate and the change in line speed under constant press-bend conditions of a certain roll press device. [Figure 10] FIG. 10 is a diagram for explaining a first feedforward control example using the first control panel. [Figure 11] FIG. 11 is a diagram for explaining a second feedforward control example using the first control panel. [Figure 12] FIG. 12 is a diagram for explaining a third feedforward control example using the first control panel. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0009] FIG. 1 is a schematic front view of a roll press device according to the first embodiment. A first pressure roller 11 and a second pressure roller 12 are a pair of upper and lower roll bites, which are installed facing each other so as to be freely movable toward and away from each other. The pair of first pressure roller 11 and second pressure roller 12 rolls the electrode plate 2 of the secondary battery, which is continuously conveyed, by sandwiching the electrode plate 2. The electrode plate 2 of the secondary battery passed through the roll press device is a sheet-like electrode material in which a slurry containing an active material is applied to a metal foil and then dried. For example, a positive electrode plate of a lithium ion secondary battery is prepared by applying a slurry containing a positive electrode active material such as lithium cobalt oxide or lithium iron phosphate to an aluminum foil. In addition, a negative electrode plate of a lithium ion secondary battery is prepared by applying a slurry containing a negative electrode active material such as graphite to a copper foil. The thickness of the electrode plate 2 passed through the roll press device is mostly the thickness of the applied active material.

[0010] The first main bearing 21 and the second main bearing 22 are provided on one side and the other side, respectively, of the rotating shaft of the first pressure roller 11, and rotatably support the rotating shaft. The third main bearing 23 and the fourth main bearing 24 are provided on one side and the other side, respectively, of the rotating shaft of the second pressure roller 12, and rotatably support the rotating shaft.

[0011] The first bend bearing portion 31 and the second bend bearing portion 32 are provided on one side and the other side, respectively, of the rotating shaft of the first pressure roller 11, and rotatably support the rotating shaft. The third bend bearing portion 33 and the fourth bend bearing portion 34 are provided on one side and the other side, respectively, of the rotating shaft of the second pressure roller 12, and rotatably support the rotating shaft.

[0012] In the example shown in FIG. 1, the first main bearing portion 21 to the fourth main bearing portion 24 and the first bend bearing portion 31 to the fourth bend bearing portion 34 are each formed of a bearing box that houses a bearing that rotatably supports the rotation shaft of the roller.

[0013] The first compression mechanism 41 is a mechanism capable of compressing the electrode plate 2 by applying a load to at least one of the first main bearing 21 and the third main bearing 23 in a direction in which the first pressure roller 11 and the second pressure roller 12 approach each other. The second compression mechanism 42 is a mechanism capable of compressing the electrode plate 2 by applying a load to at least one of the second main bearing 22 and the fourth main bearing 24 in a direction in which the first pressure roller 11 and the second pressure roller 12 approach each other.

[0014] In the first embodiment, the first compression mechanism 41 includes a first press cylinder 41a capable of applying a load to the third main bearing 23, and a first electric screw 41b capable of applying a load to the first main bearing 21. The second compression mechanism 42 includes a second press cylinder 42a capable of applying a load to the fourth main bearing 24, and a second electric screw 42b capable of applying a load to the second main bearing 22. For example, a hydraulic servo valve or a pressure reducing valve can be used to control the pressure of the first press cylinder 41a and the second press cylinder 42a. A servo motor is used to control the positions of the first electric screw 41b and the second electric screw 42b. The respective amounts of pressing down of the first electric screw 41b and the second electric screw 42b are controlled by the respective servo motors, and the loads applied by the first electric screw 41b and the second electric screw 42b to the first main bearing 21 and the second main bearing 22, respectively, are controlled.

[0015] The first bend mechanism 51 (first bend cylinder 51a in the first embodiment) is a mechanism that is provided between the first bend bearing portion 31 and the third bend bearing portion 33, and is capable of correcting the deflection of the rollers by applying a load in a direction in which the first pressure roller 11 and the second pressure roller 12 move toward and away from each other. The second bend mechanism 52 (second bend cylinder 52a in the first embodiment) is a mechanism that is provided between the second bend bearing portion 32 and the fourth bend bearing portion 34, and is capable of correcting the deflection of the rollers by applying a load in a direction in which the first pressure roller 11 and the second pressure roller 12 move toward and away from each other.

[0016] The roll gap between the first pressure roller 11 and the second pressure roller 12 is controlled by changing the pressure of the first compression mechanism 41 and / or the second compression mechanism 42 by a press pressure control unit 817a (see FIG. 5) described later. The roll deflection also changes with the change in the roll gap. The amount of roll deflection can be corrected by changing the pressure of the first bending mechanism 51 and / or the second bending mechanism 52 by a bend pressure control unit 818a (see FIG. 5) described later. At that time, the roll gap also changes, and acts in the opposite manner to the pressure change by the first compression mechanism 41 and / or the second compression mechanism 42.

[0017] The first preload mechanism 61 (first preload cylinder 61a in the example shown in FIG. 1) is a mechanism that applies a constant load to the first bend bearing portion 31 in the direction in which the first pressure roller 11 and the second pressure roller 12 move toward and away from each other. The second preload mechanism 62 (second preload cylinder 62a in the example shown in FIG. 1) is a mechanism that applies a constant load to the second bend bearing portion 32 in the direction in which the first pressure roller 11 and the second pressure roller 12 move toward and away from each other. The pressures of the first preload cylinder 61a and the second preload cylinder 62a are fixed and are always set to the same pressure.

[0018] In the example shown in Fig. 1, the first preload mechanism 61 and the second preload mechanism 62 apply a preload load equal to or greater than the weight of the first pressure roller 11 to the first bend bearing portion 31 and the second bend bearing portion 32. This appropriately presses (pulls) the first pressure roller 11 upward, reducing the effect of rattling of the roll press device. Note that the first preload mechanism 61 and the second preload mechanism 62 can be omitted.

[0019] 2 is a schematic front view of a roll press device according to embodiment 2. Differences from the configuration of embodiment 1 will be described below. In embodiment 1, a first bend cylinder 51a and a second bend cylinder 52a are provided between the upper first bend bearing portion 31 and the second bend bearing portion 32 and the lower third bend bearing portion 33 and the fourth bend bearing portion 34, and a first bend mechanism 51 and a second bend mechanism 52 are adopted that apply a load in a direction in which the first pressure roller 11 and the second pressure roller 12 move away from each other.

[0020] In the second embodiment, the first bend mechanism 51 and the second bend mechanism 52 are provided with a third bend cylinder 51b on the outside of the first bend bearing portion 31, a fourth bend cylinder 52b on the outside of the second bend bearing portion 32, a fifth bend cylinder 51c on the outside of the third bend bearing portion 33, and a sixth bend cylinder 52c on the outside of the fourth bend bearing portion 34. In the second embodiment, the third bend cylinder 51b, the fourth bend cylinder 52b, the fifth bend cylinder 51c, and the sixth bend cylinder 52c are used to apply a load in a direction in which the first pressure roller 11 and the second pressure roller 12 come into contact with each other and separate from each other. In the second embodiment, the first preload mechanism 61 and the second preload mechanism 62 are not provided.

[0021] In the second embodiment, the first compression mechanism 41 includes a first press cylinder 41a, a first magnetoscale 41c, and a first load cell 41d. In the second embodiment, a hydraulic servo valve is used for pressure control of the first press cylinder 41a. The first magnetoscale 41c detects the position of the first press cylinder 41a. In the second embodiment, a load due to the weight of the first pressure roller 11 is applied to the first main bearing portion 21. The first load cell 41d is a compression type load cell, and detects the load applied to the first main bearing portion 21. The configuration of the second compression mechanism 42 is similar to that of the first compression mechanism 41, and therefore a description thereof will be omitted. In the second embodiment, the first electric screw 41b and the second electric screw 42b are not provided.

[0022] 3 is a schematic front view of a roll press device according to embodiment 3. The following describes the differences from the configuration of embodiment 1. The first bending mechanism 51 and the second bending mechanism 52 of embodiment 3 are of the same type as the first bending mechanism 51 and the second bending mechanism 52 of embodiment 2.

[0023] The first compression mechanism 41 and the second compression mechanism 42 of the third embodiment are provided with a first electric cotter 41e and a second electric cotter 42e instead of the first electric screw 41b and the second electric screw 42b of the first embodiment. The first load cell 41d and the second load cell 42d are not provided. In general, the roll press device according to the third embodiment can be manufactured more cheaply than the roll press devices according to the first and second embodiments.

[0024] The first electric cotter 41e is provided between the first main bearing 21 and the third main bearing 23. The first electric cotter 41e includes an upper cotter fixed to the first main bearing 21 and a lower cotter fixed to the third main bearing 23. The lower surface of the upper cotter and the upper surface of the lower cotter are tapered surfaces, and the tapered surfaces are arranged to face each other. A linear servo motor is provided on the lower cotter for sliding the lower cotter in the left-right direction (the direction of the tapered surface). The height of the first electric cotter 41e can be adjusted by sliding the lower cotter left-right. In the example shown in FIG. 3, when the lower cotter slides leftward, the height of the first electric cotter 41e decreases, and when the lower cotter slides rightward, the height of the first electric cotter 41e increases. That is, the more the lower cotter slides leftward, the greater the load in the direction in which the first pressure roller 11 and the second pressure roller 12 approach each other.

[0025] The second electric cotter 42e is provided between the second main bearing portion 22 and the fourth main bearing portion 24. The second electric cotter 42e includes an upper cotter fixed to the second main bearing portion 22 and a lower cotter fixed to the fourth main bearing portion 24. The configuration of the second electric cotter 42e is similar to that of the first electric cotter 41e, and therefore a description thereof will be omitted.

[0026] 4 is a schematic side view of the roll press device 1 according to the first to third embodiments. An unwinder 13 is provided on the entry side of the pair of first pressure roller 11 and second pressure roller 12, and a winder 14 is provided on the exit side. The unwinder 13 unwinds the sheet-shaped electrode plate 2 wound in a coil shape toward the pair of first pressure roller 11 and second pressure roller 12. The winder 14 winds up the electrode plate 2 compressed by the pair of first pressure roller 11 and second pressure roller 12 into a coil shape.

[0027] The motor 15 drives the first pressure roller 11 and the second pressure roller 12. The pulse generator 16 is attached to the driving motor 15 and detects the number of rotations of the motor 15.

[0028] The thickness meter 70 is provided on the exit side of the pair of first pressure roller 11 and second pressure roller 12, and detects the thickness of the electrode plate 2 at three points, a first point, a second point, and a third point, aligned in the width direction of the electrode plate 2. The first point is set at the end of the electrode plate 2 on the side where the first compression mechanism 41 is provided. The second point is set at the center of the electrode plate 2. The third point is set at the end of the electrode plate 2 on the side where the second compression mechanism 42 is provided.

[0029] In a typical roll press device 1, a screen operated by an operator is provided on the side where the motor 15 is provided (the first compression mechanism 41 side in the first to third embodiments) and on the opposite side (the second compression mechanism 42 side in the first to third embodiments). In the following, in the first to third embodiments, the first point is referred to as the drive side, the second point is referred to as the center, and the third point is referred to as the operation side. That is, the thickness meter 70 detects the thicknesses of the drive side, center, and operation side of the electrode plate 2 after compression processing.

[0030] The thickness meter 70 may be a device that extracts the thickness of the drive side, center, and operation side by scanning one thickness detection sensor in the width direction of the electrode plate 2 and continuously detecting the thickness of the electrode plate 2.

[0031] Furthermore, the thickness meter 70 may have three thickness detection sensors fixedly installed on the drive side, the center, and the operation side, respectively, and the three thickness detection sensors may detect the thicknesses on the drive side, the center, and the operation side, respectively.

[0032] The detection method of the thickness meter 70 may be a method in which a laser sensor or an optical sensor is used to detect the distance to each of the two faces of the electrode plate 2, and the thickness is detected from the positional relationship between them. Alternatively, a magnetic sensor may be used to detect a change in eddy current to detect the distance to the outer diameter surface of the electrode plate 2, a laser sensor or an optical sensor may be used to detect the distance to the surface of the electrode plate 2 on the guide roll, and the thickness may be detected from the positional relationship between the guide roll and the surface of the electrode plate 2. The distance to the surface of the electrode plate 2 may be detected using a white light confocal sensor.

[0033] The control device 80 is a device for controlling the entire roll press device 1, and in the example shown in FIG. 4, includes a first control panel 81 and a second control panel 82. The first control panel 81 is a control panel for the press system, and the second control panel 82 is a control panel for the thickness system. A rotation pulse generated by the pulse generator 16 is input to the first control panel 81. A thickness detection value detected by the thickness meter 70 is input to the second control panel 82. The configuration described using FIG. 4 is common to the first to third embodiments.

[0034] FIG. 5 is a diagram for explaining feedback control example 1 using a first control panel 81 and a second control panel 82. Feedback control example 1 is a control used in the roll press apparatus according to embodiment 1 shown in FIG. 1. In feedback control example 1, a first press cylinder 41a and a second press cylinder 42a are used as a compression mechanism. A first bending cylinder 51a and a second bending cylinder 52a are used as a bending mechanism. The first control panel 81 includes a PLC (Programmable Logic Controller), a PC (Personal Computer), an HMI (Human Machine Interface), an actuator controller, etc. The second control panel includes a PLC, a PC, a sensor controller, etc.

[0035] The program that runs in the PLC is generated by a dedicated application in a PC and downloaded to the PLC. In addition, product information of the electrode plate 2 is input to the PLC from an MES (Manufacturing Execution System). In addition, various set values ​​input by an operator via the HMI are input to the PLC. In feedback control example 1, the set values ​​include the target thickness value of the electrode plate 2, the pressure set values ​​of the first press cylinder 41a and the second press cylinder 42a, and the pressure set values ​​of the first bend cylinder 51a and the second bend cylinder 52a. The HMI accepts inputs from the operator and displays the operating status and warnings, etc., and outputs them as voice.

[0036] 5 illustrates functional blocks realized by the first control panel 81 and the second control panel 82 related to feedback control example 1. The first control panel 81 includes a length measurement unit 811, an acquisition timing generation unit 812, a thickness measurement value acquisition unit 813, a feature amount calculation unit 814, a correction value calculation unit 815, a set value correction unit 816, a press pressure control unit 817a, a PID control unit 817b, a press pressure deviation calculation unit 817c, a bend pressure control unit 818a, a PID control unit 818b, and a bend pressure deviation calculation unit 818c. The second control panel 82 includes a thickness measurement value calculation unit 821.

[0037] A rotation pulse is input to the length measurement unit 811 from the pulse generator 16. Based on the input rotation pulse, the length measurement unit 811 estimates the rotation speeds of the first pressure roller 11 and the second pressure roller 12, and estimates the speed of the electrode plate 2 passing between the first pressure roller 11 and the second pressure roller 12. Based on the estimated speed of the electrode plate 2, the length measurement unit 811 measures the length (distance) traveled by the electrode plate 2 per unit time. The length measurement unit 811 supplies the measured length of the electrode plate 2 to the acquisition timing generation unit 812 and the thickness measurement calculation unit 821.

[0038] The thickness measurement value calculation unit 821 receives the thickness detection values ​​of the drive side, center part, and operation side from the thickness meter 70. In addition, the length of the electrode plate 2 is input from the length measurement unit 811.

[0039] When three thickness detection sensors are fixed in thickness meter 70 to detect thickness, in order to remove high-frequency thickness fluctuations that do not need to be controlled, thickness measurement calculation unit 821 averages and filters the three thickness detection values ​​in the length direction (travel direction) of electrode plate 2. In order to remove abrupt changes in the travel direction due to the pulsation of the coating pump in the coating process, it is desirable to calculate an average value of 5 mm or more in the travel direction.

[0040] For example, when thickness detection values ​​are input at 1 mm intervals, the thickness measurement calculation unit 821 calculates a moving average of five points in the running direction to obtain the measurement value. Alternatively, the thickness measurement calculation unit 821 may calculate an average of three points, excluding the two most outlying points, out of the five points detected in the running direction, to obtain the measurement value. When calculating the moving average, the thickness measurement calculation unit 821 uses the length of the electrode plate 2 input from the length measurement unit 811 as a synchronization signal. Note that detection values ​​corresponding to uncoated areas corresponding to slits in the width direction of the electrode plate 2 and areas coated on only one side are excluded.

[0041] When the thickness is detected by scanning one thickness detection sensor in the width direction of the electrode plate 2 in the thickness meter 70, the thickness measurement calculation unit 821 may calculate the average value of the detection values ​​in the respective width ranges of the drive side, the center part, and the operation side that are preset, and set it as the measurement value. Furthermore, the measurement values ​​may be averaged in the traveling direction as described above to set it as the final measurement value.

[0042] The thickness measurement calculation unit 821 calculates the driving side thickness measurement T m , the central thickness measurement T c , the measured thickness on the operating side T s is supplied to the thickness measurement value acquisition unit 813.

[0043] The acquisition timing generation unit 812 is a unit for generating a thickness measurement value, and the thickness measurement value acquisition unit 813 receives the driving side thickness measurement value T m , the central thickness measurement T c , the measured thickness on the operating side T s The timing for acquiring the measured value is generated and the generated timing is supplied to the thickness measurement acquisition unit 813.

[0044] A distance L is provided between the pressing position of the first pressure roller 11 and the second pressure roller 12 and the thickness meter 70. t (Pass line length L t) Therefore, a time lag occurs until the thickness change caused by the pressure change by the first pressure roller 11 and the second pressure roller 12 is detected by the thickness meter 70. In addition, there is a time lag t from when the pressure setting value of the compression mechanism and / or the bending mechanism is changed until the actual pressure change of the compression mechanism and / or the bending mechanism is completed. d occurs.

[0045] Among the press cylinders controlled by hydraulic servo valves, the press cylinders controlled by pressure reducing valves, the electric screw, and the electric cotter, the press cylinders controlled by hydraulic servo valves have the highest response, and the time lag of the control system is the shortest when the press cylinders controlled by hydraulic servo valves are used. d becomes smaller.

[0046] Pass line length L t and the control system time lag t d is actually measured in advance, and the actually measured value is set as a fixed value in the acquisition timing generation unit 812. The acquisition timing generation unit 812 calculates the path line length L t The length parameter L to be compared with and the control system time lag t d The acquisition timing generation unit 812 increments the length parameter L based on the length of the electrode plate 2 supplied from the length measurement unit 811, and uses a time parameter t to compare with the control system time lag t d is incremented based on the clock provided by the clock.

[0047] When at least one of the pressure set values ​​of the first press cylinder 41a, the second press cylinder 42a, the first bend cylinder 51a, and the second bend cylinder 52a is changed by the set value correction unit 816, the acquisition timing generation unit 812 resets the length parameter L and the time parameter t to zero. t and the time parameter t exceeds the control system time lag t d When it exceeds this value, the acquisition timing is supplied to the thickness measurement value acquisition unit 813.

[0048] The length parameter L is the path line length L t and the time parameter t exceeds the control system time lag t d The state where this value is exceeded is a state in which the change in thickness of the electrode plate 2 due to a change in the pressure setting value of at least one of the first press cylinder 41a, the second press cylinder 42a, the first bend cylinder 51a, and the second bend cylinder 52a is reflected in the detection value of the thickness meter 70.

[0049] On the other hand, the length parameter L is the path line length L t or the time parameter t does not exceed the control system time lag t d The state where the pressure setting value of at least one of the first press cylinder 41a, the second press cylinder 42a, the first bending cylinder 51a, and the second bending cylinder 52a is not yet reflected in the detection value of the thickness meter 70. In this state, the effect of the change in the pressure setting value on the thickness of the electrode plate 2 has not yet been confirmed.

[0050] Therefore, the length parameter L is the path line length L t and the time parameter t exceeds the control system time lag t d , and the next change in the pressure set value is put on hold until that state is reached. This avoids unnecessary or excessive changes in the pressure set values ​​of the first press cylinder 41a, the second press cylinder 42a, the first bend cylinder 51a, and the second bend cylinder 52a, and enables efficient adjustment of the pressure set values.

[0051] The thickness measurement acquisition unit 813 receives the driving side thickness measurement T m , the central thickness measurement T c , and the measured thickness on the operating side T s The acquisition timing generator 812 acquires the signal at a timing supplied thereto, and supplies the signal to the feature amount calculator 814.

[0052] The characteristic amount calculation unit 814 receives the driving side thickness measurement value T m , the central thickness measurement Tc , and the measured thickness on the operating side T s The feature amount calculation unit 814 also receives the thickness target value T t is entered.

[0053] The feature amount calculation unit 814 calculates the driving side thickness measurement value T m , the central thickness measurement T c , the measured thickness on the operating side T s , and the thickness target value T t Based on this, three deviation feature quantities defined by the following (Equation 1) to (Equation 3) are calculated as thickness feature quantities to be controlled. t-m is the thickness target value T t and the thickness measurement value T m The second feature T t-s is the thickness target value T t and the measured thickness on the operating side T s The third feature T drop is the central thickness measurement T c and the thickness measurement value T m and the measured thickness on the operating side T s It is defined as the difference between the average value of

[0054] T t-m =T t -T m ...(Formula 1) T t-s =T t -T s ...(Formula 2) T drop =T c -T ms,ave =T c -(T m +T s ) / 2...(Formula 3) First feature T t-m =0, second feature T t-s =0, the third feature T drop When = 0, the thickness measurement value T m = median thickness measurement T c = Thickness measurement value T on the operating side s = Target thickness T t The third feature T droprepresents the second-order component of the thickness profile (when the value is large, it has an upward convex parabolic shape) and changes depending on the magnitude and direction of the roll deflection.

[0055] The feature amount calculation unit 814 calculates the first feature amount T t-m , the second feature T t-s , the third feature T drop is supplied to the correction value calculation unit 815.

[0056] According to the experiments conducted by the present inventors, the first feature T t-m , the second feature T t-s , the third feature T drop It was found that there exists a relationship between the load and the strain, as defined by the following (Equation 4) to (Equation 6).

[0057] T t-m ∝(Drive load) (Equation 4) T t-s ∝(Operation side load) (Formula 5) T drop ∝A × (total press load) - B × (total bending load) - C × (total preload load) (Equation 6) Here, the total press load is the sum of the driving side press load and the operating side press load, the total bend load is the sum of the driving side bend load and the operating side bend load, and the total preload load is the sum of the driving side preload load and the operating side preload load. The driving side load is the driving side load generated by the driving side press cylinder, the driving side bend cylinder, and the driving side preload cylinder. The operating side load is the operating side load generated by the operating side press cylinder, the operating side bend cylinder, and the operating side preload cylinder.

[0058] The press cylinder load acts in a direction to apply pressure to the material being rolled, while the bend load and preload load act in a direction to reduce the pressure on the material being rolled. The preload cylinder load is set to a fixed value that ensures a pressing pressure that does not cause excessive roll deflection and that can reduce the rattle and vibration of the equipment. In other words, the preload load is not changed during thickness control. If the preload cylinder load is excessively large, it becomes difficult to control the roll deflection within the control range of the press pressure and bend pressure. In the case of equipment that does not have the first preload cylinder 61a and the second preload cylinder 62a, the preload load is zero.

[0059] In the above formula (6), A, B, and C are positive constants, and the difference between the driving side load and the operation side load of each of the total press load, the total bend load, and the total preload load is the third characteristic quantity T drop This indicates that each has a different impact on

[0060] By measuring the proportional constants of the left and right sides of each of the above (Equation 4) to (Equation 6) in advance, when the total preload load is a constant value or when a preload mechanism is not provided, the first feature quantity T t-m and the second feature T t-s and the third feature T drop The total press load and the total bend load that simultaneously make the above zero can be uniquely determined.

[0061] In feedback control example 1, each load is controlled by controlling the pressure of each cylinder. The load is calculated by cylinder diameter (constant) x cylinder pressure. From the above (Equation 4) to (Equation 6), the driving side press pressure P m , Operating side press pressure P s , Drive side bend pressure B m , operation side bend pressure B s , driving side preload pressure R m , operation side preload pressure R s , average pressing pressure P ave =(P m +P s) / 2, mean bending pressure B ave =(B m +B s ) / 2, mean preload pressure R ave =(R m +R s ) / 2 and the first feature T t-m , the second feature T t-s , the third feature T drop The following relationships (Formula 7) to (Formula 15) hold between them. Specifically, the following (Formula 7) to (Formula 9) can be derived from the above (Formula 4), the above (Formula 10) to (Formula 12) can be derived from the above (Formula 5), ​​and the following (Formula 13) to (Formula 15) can be derived from the above (Formula 6).

[0062] T t-m ∝P m ...(Formula 7) T t-m ∝-B m ...(Formula 8) T t-m ∝-R m ...(Formula 9) T t-s ∝P s ...(Equation 10) T t-s ∝-B s ...(Formula 11) T t-s ∝-R s ...(Equation 12) T drop ∝P ave ...(Equation 13) T drop ∝-B ave ...(Equation 14) T drop ∝-R ave ...(Formula 15) The proportional constants of the above (Equation 7) to (Equation 8), (Equation 10) to (Equation 11), and (Equation 13) to (Equation 14) are measured in advance. When the preload pressure is constant or when the preload mechanism is not provided, the drive side bend pressure B m and operating side bend pressure B s If the pressure difference is kept constant, the first feature value T t-m and the second feature T t-sAt the same time, the driving pressure P m and the operating pressure P s Driving side press pressure correction value ΔP m and the operation side press pressure correction value ΔP s are obtained respectively.

[0063] From the correlation shown in the above (Equation 13), the above driving side press pressure P m and the operating pressure P s The third feature value T drop The change in the third feature value T drop Based on the change in drop Average bending pressure B to make zero ave Correction value ΔB ave is obtained. Drive side bend pressure B m and operating side bend pressure B s Since the difference between the pressures is constant, the drive bend pressure B m and operating side bend pressure B s Drive side bend pressure correction value ΔB m and the operation side bend pressure correction value ΔB s is required.

[0064] The pressure of the first press cylinder 41a is the corrected driving side press pressure set value P m +ΔP m The pressure of the second press cylinder 42a is adjusted to the corrected operating pressure setting value P s +ΔP s The pressure of the first bend cylinder 51a is corrected to the driving side bend pressure set value B m +ΔB m The pressure of the second bend cylinder 52a is the corrected operation side bend pressure set value B s +ΔB s By controlling the pressure of each cylinder so that the thickness of the electrode plate 2 across the entire width is set to the target value T t can be controlled.

[0065] The correction value calculation unit 815 receives the first feature value T t-m , the second feature T t-s, the third feature T drop In addition, the drive side press pressure setting value P m , operation side press pressure setting value P s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s is supplied. Drive side press pressure setting value P m , operation side press pressure setting value P s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s Under standard conditions, the first feature T t-m , the second feature T t-s , the third feature T drop are all set to zero.

[0066] The correction value calculation unit 815 calculates the first feature amount T t-m , the second feature T t-s , the third feature T drop Based on the proportional constants of (Equation 7), (Equation 8), (Equation 10), (Equation 11), (Equation 13), and (Equation 14), the driving side press pressure correction value ΔP m , operation side press pressure correction value ΔP s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s The correction value calculation unit 815 calculates the driving side press pressure correction value ΔP m , operation side press pressure correction value ΔP s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s is supplied to the set value correction unit 816.

[0067] The set value correction unit 816 receives the driving side press pressure correction value ΔP from the correction value calculation unit 815. m , operation side press pressure correction value ΔP s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s In addition, the drive side press pressure setting value Pm , operation side press pressure setting value P s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s is supplied.

[0068] The set value correction unit 816 corrects the driving side press pressure set value P m , operation side press pressure setting value P s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s , the driving side press pressure correction value ΔP m , operation side press pressure correction value ΔP s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s Add these together to get the corrected drive side press pressure setting value P m +ΔP m , the corrected press pressure setting value P s +ΔP s , Corrected drive side bend pressure setting value B m +ΔB m , and the corrected operation side bend pressure setting value B s +ΔB s Calculate.

[0069] The set value correction unit 816 calculates the corrected driving side press pressure set value P m +ΔP m , the corrected press pressure setting value P s +ΔP s is supplied to the press pressure deviation calculation unit 817c, and the corrected drive side bend pressure setting value B m +ΔB m , Corrected operation side bend pressure setting value B s +ΔB s is supplied to the bend pressure deviation calculation unit 818c.

[0070] The press pressure deviation calculation unit 817c calculates the corrected driving side press pressure set value P m +ΔP m and the deviation between the actual pressure measurement value of the first press cylinder 41a and the corrected press pressure setting value Ps +ΔP s and the actual pressure measurement value of the second press cylinder 42a are calculated. The actual pressure measurement value of the first press cylinder 41a and the actual pressure measurement value of the second press cylinder 42a can each be estimated based on the measurement value of a valve opening gauge, for example.

[0071] The press pressure deviation calculation unit 817c supplies the calculated pressure deviation of the first press cylinder 41a and the pressure deviation of the second press cylinder 42a to the PID control unit 817b. The PID control unit 817b generates a manipulated variable for the pressure of the first press cylinder 41a and a manipulated variable for the pressure of the second press cylinder 42a based on the pressure deviation of the first press cylinder 41a and the pressure deviation of the second press cylinder 42a.

[0072] Instead of PID compensation, P compensation, PI compensation, or PD compensation may be used. The proportional term (steady-state error) can be controlled. , In I compensation The integral term can be controlled ,D compensation allows control of the differential term.

[0073] The PID control unit 817b supplies the generated manipulated variable for the pressure of the first press cylinder 41a and the manipulated variable for the pressure of the second press cylinder 42a to the press pressure control unit 817a. The press pressure control unit 817a includes an actuator, and drives each of the first press cylinder 41a and the second press cylinder 42a based on the manipulated variable for the pressure of the first press cylinder 41a and the manipulated variable for the pressure of the second press cylinder 42a.

[0074] The bend pressure deviation calculation unit 818c calculates the corrected drive side bend pressure set value B supplied from the set value correction unit 816. m +ΔB m and the deviation between the actual pressure measurement value of the first bend cylinder 51a and the corrected operating side bend pressure set value B s +ΔB s and the deviation between the actual pressure measurement value of the second bend cylinder 52a and the actual pressure measurement value of the second bend cylinder 52a are calculated.

[0075] The bend pressure deviation calculation unit 818c supplies the calculated pressure deviation of the first bend cylinder 51a and the pressure deviation of the second bend cylinder 52a to the PID control unit 818b. The PID control unit 818b generates a manipulated variable for the pressure of the first bend cylinder 51a and a manipulated variable for the pressure of the second bend cylinder 52a based on the pressure deviation of the first bend cylinder 51a and the pressure deviation of the second bend cylinder 52a.

[0076] The PID control unit 818b supplies the generated manipulated variable of the pressure of the first bend cylinder 51a and the manipulated variable of the pressure of the second bend cylinder 52a to the bend pressure control unit 818a. The bend pressure control unit 818a includes an actuator, and controls the first bend cylinder 51a and 2 Bend Cylinder 52 a respectively.

[0077] In this way, in feedback control example 1, feedback control is performed so that the press cylinder pressure maintains a set value. The operation object is the press cylinder pressure. Also, feedback control is performed so that the bend cylinder pressure maintains a set value. The operation object is the bend cylinder pressure. A correction value calculated from the thickness measurement value is added to the set value of the press cylinder pressure and the set value of the bend cylinder pressure, thereby controlling the thickness of the electrode plate 2 to the target value.

[0078] FIG. 6 is a diagram for explaining a feedback control example 2 using the first control panel 81 and the second control panel 82. The feedback control example 2 is a control used in the roll press apparatus according to the second embodiment shown in FIG. 2. In the feedback control example 2, the first press cylinder 41a and the second press cylinder 42a are used as a compression mechanism. At least one of the third bending cylinder 51b and the fifth bending cylinder 51c, and at least one of the fourth bending cylinder 52b and the sixth bending cylinder 52c are used as a bending mechanism. The differences from the feedback control example 1 shown in FIG. 5 will be described below. In the feedback control example 2, a cylinder position control unit 817d, a PID control unit 817e, and a cylinder position deviation calculation unit 817f are provided instead of the press pressure control unit 817a, the PID control unit 817b, and the press pressure deviation calculation unit 817c.

[0079] According to the experiments conducted by the present inventors, the first feature T t-m , the second feature T t-s , the third feature T drop and the driving side press cylinder position G m , Operation side press cylinder position G s , average press cylinder position G ave =(G m +G s ) / 2, the relationship defined by the following (Equation 16) to (Equation 18) exists.

[0080] T t-m ∝G m ...(Equation 16) T t-s ∝G s ...(Formula 17) T drop ∝-G ave ...(Formula 18) The thickness of the electrode plate 2 does not increase or decrease only due to changes in the position of the press cylinder, but the amount of elastic deformation of the first pressure roller 11 and the second pressure roller 12 caused by changes in the reaction force from the electrode plate 2 must also be taken into consideration.

[0081] Drive side press cylinder position G m , Operation side press cylinder position Gs , the average press cylinder position G ave and the first feature value T t-m , the second feature T t-s , the third feature T drop The correlation between the above is experimentally determined in advance.

[0082] Drive side bend pressure B m and operating side bend pressure B s If the pressure difference is kept constant, the first feature value T t-m and the second feature T t-s At the same time, the driving press cylinder position G becomes zero. m and the operating side press cylinder position G s Drive side press cylinder position correction value ΔG m and the operating side press cylinder position correction value ΔG s are obtained respectively.

[0083] From the correlation shown in the above (Equation 18), the driving side press cylinder position G m and the operating side press cylinder position G s The third feature value T drop The change in ΔT drop From the correlation shown in the above (Equation 14), the change amount ΔT drop The third feature T drop +ΔT drop Average bending pressure B to make zero ave Correction value ΔB ave is required.

[0084] The cylinder position of the first press cylinder 41a is the driving side press cylinder position setting value G after correction. m +ΔG m The cylinder position of the second press cylinder 42a is adjusted to the corrected operating side press cylinder position setting value G s +ΔG s The pressure of the third bend cylinder 51b and the fifth bend cylinder 51c is set to the corrected drive side bend pressure set value B m +ΔB mThe pressure of the fourth bend cylinder 52b and the sixth bend cylinder 52c is the corrected operation side bend pressure set value B s +ΔB s By controlling the cylinder positions of the first press cylinder 41a and the second press cylinder 42a and the pressures of the third bend cylinder 51b, the fifth bend cylinder 51c, the fourth bend cylinder 52b, and the sixth bend cylinder 52c so that the thickness of the electrode plate 2 over the entire width is set to the target value T t can be controlled.

[0085] The correction value calculation unit 815 receives the first feature value T t-m , the second feature T t-s , the third feature T drop In addition, the drive side press cylinder position setting value G input by the operator via the HMI is m , operation side press cylinder position setting value G s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s is supplied. Drive side press cylinder position setting value G m , operation side press cylinder position setting value G s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s Under standard conditions, the first feature T t-m , the second feature T t-s , the third feature T drop are all set to zero.

[0086] The correction value calculation unit 815 calculates the first feature amount T t-m , the second feature T t-s , the third feature T drop Based on the proportional constants of (Equation 16), (Equation 17), (Equation 18), and (Equation 14), the driving side press cylinder position correction value ΔG m , operation side press cylinder position correction value ΔG s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB sThe correction value calculation unit 815 calculates the calculated driving side press cylinder position correction value ΔG m , operation side press cylinder position correction value ΔG s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s is supplied to the set value correction unit 816.

[0087] The set value correction unit 816 receives the driving side press cylinder position correction value ΔG m , operation side press cylinder position correction value ΔG s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s In addition, the drive side press cylinder position setting value G input by the operator via the HMI is m , operation side press cylinder position setting value G s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s is supplied.

[0088] The set value correction unit 816 corrects the drive side press cylinder position set value G m , operation side press cylinder position setting value G s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s , the driving side press cylinder position correction value ΔG m , operation side press cylinder position correction value ΔG s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s Add these values ​​together to obtain the corrected drive side press cylinder position setting value G m +ΔG m , the corrected press cylinder position setting value G s +ΔG s , Corrected drive side bend pressure setting value B m +ΔB m , and the corrected operation side bend pressure setting value B s +ΔB s Calculate.

[0089] The set value correction unit 816 calculates the corrected driving side press cylinder position set value G m +ΔG m , the corrected press cylinder position setting value G s +ΔG s is supplied to the cylinder position deviation calculation unit 817f, and the corrected drive side bend pressure setting value B m +ΔB m , Corrected operation side bend pressure setting value B s +ΔB s is supplied to the bend pressure deviation calculation unit 818c.

[0090] The cylinder position deviation calculation unit 817f calculates the corrected driving side press cylinder position set value G m +ΔG m The cylinder position deviation calculation unit 817f calculates the deviation between the actual cylinder position of the first press cylinder 41a measured by the first magnet scale 41c and the operating side press cylinder position set value G s +ΔG s and the deviation between the actual value of the cylinder position of the second press cylinder 42a measured by the second magnetoscale 42c is calculated.

[0091] The cylinder position deviation calculation unit 817f supplies the calculated cylinder position deviation of the first press cylinder 41a and the cylinder position deviation of the second press cylinder 42a to a PID control unit 817e. The PID control unit 817e generates a manipulated variable for the pressure of the first press cylinder 41a and a manipulated variable for the pressure of the second press cylinder 42a, based on the cylinder position deviation of the first press cylinder 41a and the cylinder position deviation of the second press cylinder 42a.

[0092] The PID control unit 817e supplies the generated manipulated variable for the pressure of the first press cylinder 41a and the manipulated variable for the pressure of the second press cylinder 42a to the cylinder position control unit 817d. The cylinder position control unit 817d includes an actuator, and drives each of the first press cylinder 41a and the second press cylinder 42a based on the manipulated variable for the pressure of the first press cylinder 41a and the manipulated variable for the pressure of the second press cylinder 42a.

[0093] In feedback control example 2, the third bend cylinder 51b, the fifth bend cylinder 51c, the fourth bend cylinder 52b, and the sixth bend cylinder 52c are controlled as the bending mechanism. However, since this is basically the same as controlling the first bend cylinder 51a and the second bend cylinder 52a in feedback control example 1, a description thereof will be omitted.

[0094] In this way, in the feedback control example 2, the pressure of the press cylinder is not feedback-controlled to maintain a set value as in the feedback control example 1, but the position of the press cylinder is feedback-controlled to maintain a set value. position In the feedback control example 2, feedback control is also performed so that the pressure of the bend cylinder is maintained at a set value. The operation target is the pressure of the bend cylinder. A correction value calculated from the thickness measurement value is added to the set value of the press cylinder position and the set value of the bend cylinder pressure, thereby controlling the thickness of the electrode plate 2 to the target value.

[0095] 7 is a diagram for explaining feedback control example 3 using the first control panel 81 and the second control panel 82. Feedback control example 3 is a control used in the roll press apparatus according to embodiment 1 shown in FIG. 1. In feedback control example 3, a first electric screw 41b and a second electric screw 42b are used as a compression mechanism. Note that a sufficiently large pressure (fixed value) is applied to the first press cylinder 41a and the second press cylinder 42a so that the positions of the cylinders do not change due to position control of the first electric screw 41b and the second electric screw 42b.

[0096] A first bending cylinder 51a and a second bending cylinder 52a are used as a bending mechanism. Below, differences from feedback control example 1 shown in Fig. 5 will be described. In feedback control example 3, a screw position control unit 817g, a PID control unit 817h, and a screw position deviation calculation unit 817i are provided instead of the press pressure control unit 817a, the PID control unit 817b, and the press pressure deviation calculation unit 817c.

[0097] According to the experiments conducted by the present inventors, the first feature T t-m , the second feature T t-s , the third feature T drop and drive side electric screw position D m , Operation side electric screw position D s , average electric screw position D ave =(D m +D s ) / 2, the relationship defined by the following (Equation 19) to (Equation 21) exists.

[0098] T t-m ∝D m ...(Formula 19) T t-s ∝D s ...(Formula 20) T drop ∝-D ave ...(Formula 21) The thickness of the electrode plate 2 does not increase or decrease only due to the change in the position of the electric screw, but the amount of elastic deformation of the first pressure roller 11 and the second pressure roller 12 caused by the change in the reaction force from the electrode plate 2 must also be taken into consideration.

[0099] Drive side electric screw position D m , Operation side electric screw position D s , average electric screw position D ave and the first feature value T t-m , the second feature T t-s , the third feature T drop The correlation between the above is experimentally determined in advance.

[0100] When the preload pressure is constant or when the preload mechanism is not installed, the drive side bend pressure B m and operating side bend pressure B s If the pressure difference is kept constant, the first feature value T t-m and the second feature T t-s The driving screw position D becomes zero at the same time. m and the operating side electric screw position D s Drive side electric screw position correction value ΔD m and the operating side electric screw position correction value ΔD s are obtained respectively.

[0101] From the correlation shown in the above (Equation 21), the driving side electric screw position D m and the operating side electric screw position D s The third feature value T drop The change in ΔT drop From the correlation shown in the above (Equation 14), the change amount ΔT drop The third feature T drop +ΔT drop Average bending pressure B to make zero ave Correction value ΔB ave is required.

[0102] The position of the first electric screw 41b is the corrected driving side electric screw position setting value D m +ΔD m The position of the second electric screw 42b is corrected to the set value D s +ΔD s The pressure of the first bend cylinder 51a is corrected to the driving side bend pressure set value B m +ΔB m The pressure of the second bend cylinder 52a is the corrected operation side bend pressure set value B s +ΔB s By controlling the positions of the first electric screw 41b and the second electric screw 42b and the pressures of the first bending cylinder 51a and the second bending cylinder 52a so that the thickness of the electrode plate 2 over the entire width is set to the target value T t can be controlled.

[0103] The correction value calculation unit 815 receives the first feature value T t-m , the second feature T t-s , the third feature T drop In addition, the drive side electric screw position setting value D input by the operator via the HMI is m , Operation side electric screw position setting value D s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s is supplied. Drive side electric screw position setting value D m , Operation side electric screw position setting value D s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s Under standard conditions, the first feature T t-m , the second feature T t-s , the third feature T drop are all set to zero.

[0104] The correction value calculation unit 815 calculates the first feature amount T t-m , the second feature T t-s , the third feature T drop Based on the proportional constants of (Equation 19), (Equation 20), (Equation 21), and (Equation 14), the driving side electric screw position correction value ΔD m , Operation side electric screw position correction value ΔD s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s The correction value calculation unit 815 calculates the calculated driving side electric screw position correction value ΔD m , Operation side electric screw position correction value ΔD s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s is supplied to the set value correction unit 816.

[0105] The set value correction unit 816 receives the drive side electric screw position correction value ΔD m, Operation side electric screw position correction value ΔD s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s In addition, the drive side electric screw position setting value D input by the operator via the HMI is m , Operation side electric screw position setting value D s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s is supplied.

[0106] The set value correction unit 816 corrects the drive side electric screw position set value D m , Operation side electric screw position setting value D s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s , the driving side electric screw position correction value ΔD m , Operation side electric screw position correction value ΔD s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s Add these to get the corrected drive side electric screw position setting value D m +ΔD m , the corrected setting value of the electric screw position on the operating side D s +ΔD s , Corrected drive side bend pressure setting value B m +ΔB m , and the corrected operation side bend pressure setting value B s +ΔB s Calculate.

[0107] The set value correction unit 816 calculates the corrected drive side electric screw position set value D m +ΔD m , the corrected setting value of the electric screw position on the operating side D s +ΔD s is supplied to the screw position deviation calculation unit 817i, and the corrected drive side bend pressure setting value B m +ΔB m , Corrected operation side bend pressure setting value B s +ΔB sis supplied to the bend pressure deviation calculation unit 818c.

[0108] The screw position deviation calculation unit 817i calculates the corrected driving side electric screw position set value D supplied from the set value correction unit 816. m +ΔD m The screw position deviation calculation unit 817i calculates the deviation between the measured value of the position of the first electric screw 41b and the corrected set value of the operating side electric screw position D s +ΔD s and the deviation between the measured value of the position of the second electric screw 42b.

[0109] The screw position control section 817g includes servo motors for pressing down the first electric screw 41b and the second electric screw 42b. The amount of change in the positions of the first electric screw 41b and the second electric screw 42b can be calculated from the rotation speed of each servo motor.

[0110] The screw position deviation calculation unit 817i supplies the calculated position deviation of the first electric screw 41b and the position deviation of the second electric screw 42b to a PID control unit 817h. The PID control unit 817h generates an operation amount for the rotation of the servo motor for the first electric screw 41b and an operation amount for the rotation of the servo motor for the second electric screw 42b based on the position deviation of the first electric screw 41b and the position deviation of the second electric screw 42b.

[0111] The PID control unit 817h supplies the generated manipulated variable of the rotation of the servo motor for the first electric screw 41b and the manipulated variable of the rotation of the servo motor for the second electric screw 42b to the screw position control unit 817g. The screw position control unit 817g drives the servo motor for the first electric screw 41b and the servo motor for the second electric screw 42b based on the manipulated variable of the rotation of the servo motor for the first electric screw 41b and the manipulated variable of the rotation of the servo motor for the second electric screw 42b.

[0112] Thus, in Feedback Control Example 3, instead of feedback controlling the press cylinder pressure to maintain a set value as in Feedback Control Example 1, feedback controlling is performed to feedback control the electric screw position to maintain a set value. The object of operation is the servo motor rotation speed. In Feedback Control Example 3, feedback controlling is also performed to feedback control the bend cylinder pressure to maintain a set value. The object of operation is the bend cylinder pressure. A correction value calculated from the thickness measurement value is added to the set value of the electric screw position and the set value of the bend cylinder pressure, thereby controlling the thickness of the electrode plate 2 to a target value.

[0113] FIG. 8 is a diagram for explaining feedback control example 4 using a first control panel 81 and a second control panel 82. Feedback control example 4 is a control used in the roll press apparatus according to embodiment 3 shown in FIG. 3. In feedback control example 4, a first electric cotter 41e and a second electric cotter 42e are used as a compression mechanism. Note that a sufficiently large pressure (fixed value) is applied to the first press cylinder 41a and the second press cylinder 42a so that the positions of the cylinders do not change due to height control of the first electric cotter 41e and the second electric cotter 42e.

[0114] At least one of the third bend cylinder 51b and the fifth bend cylinder 51c, and at least one of the fourth bend cylinder 52b and the sixth bend cylinder 52c are used as the bending mechanism. Below, differences from Feedback Control Example 1 shown in Fig. 5 will be explained. In Feedback Control Example 4, a cotter height control unit 817j, a PID control unit 817k, and a cotter height deviation calculation unit 817l are provided instead of the press pressure control unit 817a, the PID control unit 817b, and the press pressure deviation calculation unit 817c.

[0115] When the first electric cotter 41e and the second electric cotter 42e are in contact with the first press cylinder 41a and the second press cylinder 42a, and the first pressure roller 11 and the second pressure roller 12 are in contact with the electrode plate 2, a portion of the press load from the first press cylinder 41a and the second press cylinder 42a is distributed to the first electric cotter 41e and the second electric cotter 42e, so that (the load acting on the electrode plate 2) is expressed as (the press load) - (the load acting on the cotter).

[0116] When the pressure of the first press cylinder 41a and the second press cylinder 42a is constant, the press load is constant. In this state, the load acting on the electrode plate 2 can be changed by changing the cotter height to change the load acting on the cotter. It is difficult to measure the change in the load acting on each of the first electric cotter 41e and the second electric cotter 42e due to the change in the height of each of the first electric cotter 41e and the second electric cotter 42e.

[0117] According to the experiments conducted by the present inventors, the first feature T t-m , the second feature T t-s , the third feature T drop and the height of the driving cotter K m , height of electric cotter on operating side K s , average motorized cotter height K ave =(K m +K s ) / 2, the relationship defined by the following (Equation 22) to (Equation 24) exists.

[0118] T t-m ∝K m ...(Formula 22) T t-s ∝K s ...(Formula 23) T drop ∝-K ave ...(Formula 24) Drive side electric cotter height K m , height of electric cotter on operating side K s , average motorized cotter height K ave and the first feature value T t-m , the second feature T t-s, the third feature T drop The correlation between the above is experimentally determined in advance.

[0119] Drive side bend pressure B m and operating side bend pressure B s If the pressure difference is kept constant, the first feature value T t-m and the second feature T t-s The height of the driving cotter K becomes zero at the same time. m and the height of the electric cotter on the operating side K s Drive side electric cotter height correction value ΔK m and the height correction value ΔK of the electric cotter on the operating side s are obtained respectively.

[0120] From the correlation shown in the above (Equation 24), the height of the driving cotter K m and the height of the electric cotter on the operating side K s The third feature value T drop The change in ΔT drop From the correlation shown in the above (Equation 14), the change amount ΔT drop The third feature T drop +ΔT drop Average bending pressure B to make zero ave Correction value ΔB ave is required.

[0121] The height of the first electric cotter 41e is the corrected drive side electric cotter height setting value K m +ΔK m The height of the second electric cotter 42e is corrected to the operating side electric cotter height setting value K s +ΔK s The pressure of the third bend cylinder 51b and the fifth bend cylinder 51c is set to the corrected drive side bend pressure set value B m +ΔB m The pressure of the fourth bend cylinder 52b and the sixth bend cylinder 52c is the corrected operation side bend pressure set value B s +ΔB sBy controlling the heights of the first electric cotter 41e and the second electric cotter 42e and the pressures of the third bend cylinder 51b, the fifth bend cylinder 51c, the fourth bend cylinder 52b, and the sixth bend cylinder 52c, respectively, the thickness of the electrode plate 2 over the entire width is set to the target value T t can be controlled.

[0122] The correction value calculation unit 815 receives the first feature value T t-m , the second feature T t-s , the third feature T drop The height setting value K of the driving electric cotter input by the operator via the HMI is also provided. m , operation side electric cotter height setting value K s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s is supplied. Drive side electric cotter height setting value K m , operation side electric cotter height setting value K s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s Under standard conditions, the first feature T t-m , the second feature T t-s , the third feature T drop are all set to zero.

[0123] The correction value calculation unit 815 calculates the first feature amount T t-m , the second feature T t-s , the third feature T drop Based on the proportional constants of (Equation 22), (Equation 23), (Equation 24), and (Equation 14), the driving side electric cotter height correction value ΔK m , operation side electric cotter height correction value ΔK s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s The correction value calculation unit 815 calculates the calculated driving side electric cotter height correction value ΔK m , operation side electric cotter height correction value ΔK s , Drive side bend pressure correction value ΔB m, and the operation side bend pressure correction value ΔB s is supplied to the set value correction unit 816.

[0124] The set value correction unit 816 receives the driving side electric cotter height correction value ΔK from the correction value calculation unit 815. m , operation side electric cotter height correction value ΔK s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s The height setting value K of the driving electric cotter input by the operator via the HMI is also provided. m , operation side electric cotter height setting value K s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s is supplied.

[0125] The set value correction unit 816 corrects the drive side electric cotter height set value K m , operation side electric cotter height setting value K s , Drive side bend pressure setting value B m , and operation side bend pressure setting value B s , the driving side electric cotter height correction value ΔK m , operation side electric cotter height correction value ΔK s , Drive side bend pressure correction value ΔB m , and the operation side bend pressure correction value ΔB s Add these values ​​together to get the corrected drive side electric cotter height setting value K m +ΔK m , the corrected setting value of the electric cotter height on the operating side K s +ΔK s , Corrected drive side bend pressure setting value B m +ΔB m , and the corrected operation side bend pressure setting value B s +ΔB s Calculate.

[0126] The set value correction unit 816 calculates the corrected drive side electric cotter height set value K m +ΔK m , the corrected setting value of the electric cotter height on the operating side K s +ΔK sis supplied to the cotter height deviation calculation unit 817l, and the corrected drive side bend pressure setting value B m +ΔB m , Corrected operation side bend pressure setting value B s +ΔB s is supplied to the bend pressure deviation calculation unit 818c.

[0127] The cotter height deviation calculation unit 817l calculates the drive side electric cotter height setting value K after correction supplied from the setting value correction unit 816. m +ΔK m The cotter height deviation calculation unit 817l calculates the deviation between the measured height of the first electric cotter 41e and the corrected electric cotter height setting value K s +ΔK s The deviation between this and the measured value of the height of the second electric cotter 42e is calculated.

[0128] The cotter height control section 817j includes linear servo motors for sliding the lower cotters of the first electric cotter 41e and the second electric cotter 42e in the left-right direction. The amount of change in the height of each of the first electric cotter 41e and the second electric cotter 42e can be calculated from the amount of movement of each linear servo motor. Note that a distance meter may be provided between the first main bearing 21 and the third main bearing 23 to measure the height of the first electric cotter 41e, and a distance meter may be provided between the second main bearing 22 and the fourth main bearing 24 to measure the height of the second electric cotter 42e.

[0129] The cotter height deviation calculation unit 817l supplies the calculated height deviation of the first electric cotter 41e and the height deviation of the second electric cotter 42e to a PID control unit 817k. The PID control unit 817k generates an operation amount for the movement of the linear servo motor for the first electric cotter 41e and an operation amount for the movement of the linear servo motor for the second electric cotter 42e based on the height deviation of the first electric cotter 41e and the height deviation of the second electric cotter 42e.

[0130] The PID control unit 817k supplies the generated manipulated variable for the movement of the linear servo motor for the first electric cotter 41e and the manipulated variable for the movement of the linear servo motor for the second electric cotter 42e to a cotter height control unit 817j. The cotter height control unit 817j drives the linear servo motor for the first electric cotter 41e and the linear servo motor for the second electric cotter 42e based on the manipulated variable for the movement of the linear servo motor for the first electric cotter 41e and the manipulated variable for the movement of the linear servo motor for the second electric cotter 42e.

[0131] In feedback control example 4, the third bend cylinder 51b, the fifth bend cylinder 51c, the fourth bend cylinder 52b, and the sixth bend cylinder 52c are controlled as the bending mechanism. However, since this is basically the same as controlling the first bend cylinder 51a and the second bend cylinder 52a in feedback control example 1, a description thereof will be omitted.

[0132] Thus, in Feedback Control Example 4, instead of feedback controlling the press cylinder pressure to maintain a set value as in Feedback Control Example 1, feedback control is performed to feedback control the height of the electric cotter to maintain a set value. The controlled object is the movement amount of the linear servo motor. In Feedback Control Example 4, feedback control is also performed to feedback control the pressure of the bending cylinder to maintain a set value. The controlled object is the pressure of the bending cylinder. A correction value calculated from the thickness measurement value is added to the set value of the electric cotter height and the set value of the bending cylinder pressure, thereby controlling the thickness of the electrode plate 2 to a target value.

[0133] When hydraulic cylinders are used for the above-mentioned first press cylinder 41a, second press cylinder 42a, first bend cylinder 51a, second bend cylinder 52a, third bend cylinder 51b, fourth bend cylinder 52b, fifth bend cylinder 51c, and sixth bend cylinder 52c, it is preferable to install hydraulic control equipment as close as possible to the hydraulic cylinders. In addition, it is preferable to use a hydraulic servo valve with a high pressure control speed as the hydraulic control equipment. This makes it possible to prevent pressure hunting and delays in pressure response caused by pressure changes in the hydraulic piping due to pressure changes in the hydraulic cylinders.

[0134] However, in the method shown in Feedback Control Examples 1 to 4, in which the thickness of the electrode plate 2 during transportation is measured by a thickness meter 70 and the thickness of the electrode plate 2 is corrected by feedback control, it is difficult to accurately correct the thickness change when the transport line accelerates or decelerates. It is possible to slow down the speed of the transport line when accelerating or decelerating, but in that case, production efficiency decreases. Therefore, a method is introduced in which the thickness change of the electrode plate 2 due to the speed change of the transport line is predicted and the thickness of the electrode plate 2 is corrected by feedforward control.

[0135] Fig. 9 is a plot of the relationship between the change in line speed and the change in thickness of the electrode plate 2 under constant press-bend conditions of a certain roll press device 1. The horizontal axis indicates the line speed [mpm], and the vertical axis indicates the average thickness width [μm] of the electrode plate 2. As shown in Fig. 9, it can be seen that the faster the line speed, the thicker the electrode plate 2 becomes.

[0136] FIG. 10 is a diagram for explaining feedforward control example 1 using the first control panel 81. Feedforward control example 1 is control used in the roll press apparatus according to embodiment 1 shown in FIG. 1. In feedforward control example 1, the first press cylinder 41a and the second press cylinder 42a are used as a compression mechanism. In this specification, in order to simplify the feedforward control, a bending mechanism is not used in the feedforward control.

[0137] 10 illustrates functional blocks realized by the first control panel 81 related to feedforward control example 1. The first control panel 81 includes a line speed setting change unit 819, a line speed control unit 8110, a correction value calculation unit 815, a setting value correction unit 816, a press pressure control unit 817a, a PID control unit 817b, and a press pressure deviation calculation unit 817c.

[0138] The line speed control unit 8110 controls the rotational speed of the unwinder 13, the rotational speed of the first pressure roller 11 and the second pressure roller 12, and the rotational speed of the winder 14 based on the line speed command value supplied from the line speed setting change unit 819.

[0139] A line speed set by an operator is input to the line speed setting change unit 819. The acceleration during acceleration and the deceleration during deceleration of the conveying line are basically set in advance by the manufacturer of the roll press device 1. Note that the acceleration during acceleration and the deceleration during deceleration may be set in a specification that allows the user to change the settings.

[0140] In feedforward control example 1, a change in thickness of the electrode plate 2 due to a change in line speed is predicted, the press load required to maintain a constant thickness of the electrode plate 2 is calculated, and the press load is changed by feedforward control. By experimentally investigating the relationship between the line speed and the thickness of the electrode plate 2, it is possible to predict an appropriate press pressure with high accuracy.

[0141] The acceleration or deceleration of the line speed is α [m / s 2 ], the line speed V S seconds after the start of acceleration or deceleration s is the speed V0 at the start of acceleration or deceleration, and the change in line speed ΔV S seconds after the start of acceleration or deceleration s Using the above, the change in line speed S seconds after the start of acceleration or deceleration, ΔV s can be defined as follows (Equation 26).

[0142] V s =V0+ΔV s=V0+α×S (Formula 25) ΔV s =V s -V0=α×S (Formula 26) As shown in Figure 9, the change in line speed after S seconds, ΔV s and the average thickness T of the electrode plate 2 in the width direction. ave The change in ΔT ave Since there is a proportional relationship between and , the following relationship (Equation 27) holds.

[0143] ΔT ave =D×ΔV s ...(Formula 27) D is the proportionality constant.

[0144] Change in line speed ΔV and average thickness T ave The change in ΔT ave The relationship may be experimentally determined and may be fitted with a multidimensional function, an exponential function, or a logarithmic function.

[0145] In addition, the average value L of the press load acting on the electrode plate 2 in the width direction ave (hereinafter referred to as the linear pressure) and the average thickness after pressing T ave Since there is a proportional relationship between the linear pressure and the change in linear pressure, ΔL ave and the average thickness T ave The change in ΔT ave The following relationship (Equation 28) holds between them.

[0146] ΔT ave = E × ΔL ave ...(Formula 28) E is the proportionality constant.

[0147] Average thickness T after S seconds from the start of acceleration or deceleration ave The change in ΔT ave,s Linear pressure correction value ΔL to make zero ave,s From the above relationships (Equation 26), (Equation 27), and (Equation 28), ΔV s and ΔT ave can be obtained by removing the above and using the following (Equation 29).

[0148] ΔL ave,s ={(D×α) / E}×S (Formula 29) Linear pressure during acceleration or deceleration is L ave,0 When the linear pressure after S seconds is L ave,0 +ΔL ave,s By feedforward controlling the press mechanism so that the thickness of the electrode plate 2 changes due to changes in the line speed, it is possible to reduce the change in thickness of the electrode plate 2 caused by changes in the line speed.

[0149] In the feedforward control example 1, the positions of the first electric screw 41b and the second electric screw 42b are kept constant, and the pressure of the first press cylinder 41a and the second press cylinder 42a is changed to change the press load acting on the electrode plate 2. The driving side press pressure P m and the operating pressure P s The average pressing pressure P ave =(P m +P s ) / 2 change ΔP ave and the average thickness T of the electrode plate 2 ave The change in ΔT ave Since there is a proportional relationship between the pressure and the average pressure P ave The change in ΔP ave and the average thickness T ave The change in ΔT ave The following relationship (Equation 30) holds between them.

[0150] ΔT ave = F × ΔP ave ...(Formula 30) F is the proportionality constant.

[0151] Average thickness T after S seconds from the start of acceleration or deceleration ave The change in ΔT ave,s The average pressure P to make zero ave Correction value ΔP ave,s From the above relationships (Equation 26), (Equation 27), and (Equation 30), ΔV s and ΔT ave can be obtained by removing the above and using the following (Equation 31).

[0152] ΔP ave,s={(D×α) / F}×S (Formula 31) The average press pressure during acceleration or deceleration is P ave,0 Then, the average press pressure after S seconds is P ave,0 +ΔP ave,s By feedforward controlling the pressures of the first press cylinder 41a and the second press cylinder 42a so that the thickness of the electrode plate 2 is equal to or greater than the line speed, it is possible to suppress a change in the thickness of the electrode plate 2 caused by a change in the line speed.

[0153] The driving pressure P during the acceleration or deceleration period of the conveyor line m and the operating pressure P s The pressure difference during the acceleration or deceleration may basically be the same as before the acceleration or deceleration. However, if the change in thickness of the electrode plate 2 caused by the change in line speed differs between the driving side and the operating side due to the difference in rigidity between the driving side and the operating side of the roll press device 1, the pressure difference during the acceleration or deceleration period may be changed.

[0154] Before the start of acceleration of the transport line, the correction value calculation unit 815 is supplied with the acceleration start time, the acceleration end time, the line speed V0 at the start of acceleration, and the acceleration α from the line speed setting change unit 819. For example, when the roll press apparatus 1 is started and when the line speed is changed during startup, these pieces of information are supplied from the line speed setting change unit 819. In addition, before the start of deceleration of the transport line, the correction value calculation unit 815 is supplied with the deceleration start time, the deceleration end time, the line speed V0 at the start of deceleration, and the deceleration α from the line speed setting change unit 819.

[0155] The correction value calculation unit 815 calculates the change in the line speed S seconds after the start of acceleration, ΔV, based on the line speed V0 at the start of acceleration and the acceleration α, as expressed in (Equation 26) above. s The correction value calculation unit 815 calculates the calculated change amount ΔV s Substituting this into Equation 27 above, the average thickness T after S seconds from the start of acceleration is obtained. ave The change in ΔT ave,s The correction value calculation unit 815 predicts the average thickness T ave The change in ΔT ave,s The average pressure P to make zeroave Correction value ΔP ave,s Calculate.

[0156] In the example shown in FIG. 10, the correction value calculation unit 815 calculates the average pressing pressure P ave Correction value ΔP 0.1 , ΔP 0.2 , , ΔP tend Calculate the average press pressure P ave Correction value ΔP 0.1 , ΔP 0.2 , , ΔP tend is supplied to the set value correction unit 816.

[0157] The set value correction unit 816 receives the average pressing pressure P ave Correction value ΔP 0.1 , ΔP 0.2 , , ΔP tend The set value correction unit 816 applies a correction value ΔP to the press pressure set value P0 at the start of acceleration. 0.1 , ΔP 0.2 , , ΔP tend Add these together to get the corrected press pressure setting value P0+ΔP 0.1 , P0+ΔP 02 , , P0+ΔP tend The press pressure set value P0 at the start of acceleration is, for example, the press pressure set value P input by the operator via the HMI. The set value correction unit 816 calculates the corrected press pressure set value P0+ΔP 0.1 , P0+ΔP 02 , , P0+ΔP tend is supplied to the press pressure deviation calculation unit 817c.

[0158] The press pressure deviation calculation unit 817c calculates the corrected press pressure set value P0+ΔP 0.1 , P0+ΔP 02 , , P0+ΔP tendThe press pressure deviation calculation unit 817c calculates the deviation between the press pressure set value P0+ΔP assigned to the first press cylinder 41a and the actual pressure measurement value of the first press cylinder 41a at each time. 0.1 , P0+ΔP 02 , , P0+ΔP tend The deviation between the press pressure set value allocated to the second press cylinder 42a and the actual pressure measurement value of the second press cylinder 42a is calculated at each time. The actual pressure measurement value of the first press cylinder 41a and the actual pressure measurement value of the second press cylinder 42a can each be estimated based on the measurement value of a valve opening gauge, for example.

[0159] The press pressure deviation calculation unit 817c supplies the calculated pressure deviation of the first press cylinder 41a and the pressure deviation of the second press cylinder 42a to the PID control unit 817b. The PID control unit 817b generates a manipulated variable for the pressure of the first press cylinder 41a and a manipulated variable for the pressure of the second press cylinder 42a based on the pressure deviation of the first press cylinder 41a and the pressure deviation of the second press cylinder 42a.

[0160] The PID control unit 817b supplies the generated manipulated variable for the pressure of the first press cylinder 41a and the manipulated variable for the pressure of the second press cylinder 42a to the press pressure control unit 817a. The press pressure control unit 817a includes an actuator, and drives each of the first press cylinder 41a and the second press cylinder 42a based on the manipulated variable for the pressure of the first press cylinder 41a and the manipulated variable for the pressure of the second press cylinder 42a. Although the above explanation has been given assuming acceleration, the same control is also applied during deceleration.

[0161] The delay time from when the press pressure setting is changed until the actual press pressure changes (time lag t e ) must be taken into consideration. Therefore, the line speed setting change unit 819 determines the time lag t eA command value for changing the line speed is supplied to the line speed control unit 8110 with a timing delayed by a time corresponding to the change in the line speed. This makes it possible to change the operation of the actuator more appropriately in response to changes in the line speed, and to correct the thickness of the electrode plate 2 with high accuracy. As described above, it is desirable to use a highly responsive hydraulic servo valve for pressure control of the first press cylinder 41a and the second press cylinder 42a.

[0162] In this way, in feedforward control example 1, the change in thickness of the electrode plate 2 due to a change in line speed is predicted, the press pressure required to maintain a constant thickness of the electrode plate 2 is calculated, and the press pressure is changed by feedforward control. This makes it possible to suppress the change in thickness of the electrode plate 2 during the acceleration or deceleration period of the conveyor line with high accuracy.

[0163] FIG. 11 is a diagram for explaining feedforward control example 2 using the first control panel 81. Feedforward control example 2 is control used in the roll press apparatus according to embodiment 2 shown in FIG. 2. In feedforward control example 2, the first press cylinder 41a and the second press cylinder 42a are used as a compression mechanism. Below, differences from feedforward control example 1 shown in FIG. 10 will be described. In feedforward control example 2, a cylinder position control unit 817d, a PID control unit 817e, and a cylinder position deviation calculation unit 817f are provided instead of the press pressure control unit 817a, the PID control unit 817b, and the press pressure deviation calculation unit 817c.

[0164] In feedforward control example 2, the positions of the first electric screw 41b and the second electric screw 42b are kept constant, and the pressure of the first press cylinder 41a and the second press cylinder 42a is changed to change the press load acting on the electrode plate 2. The cylinder position of the first press cylinder 41a is measured by a first magnetoscale 41c, and the pressure of the first press cylinder 41a is controlled so that the cylinder position of the first press cylinder 41a is maintained at a set value. Similarly, the cylinder position of the second press cylinder 42a is measured by a second magnetoscale 42c, and the pressure of the second press cylinder 42a is controlled so that the cylinder position of the second press cylinder 42a is maintained at a set value. Drive side press cylinder position G m and the operating side press cylinder position G s Average press cylinder position G ave =(G m +G s ) / 2 change in ΔG ave and the average thickness T of the electrode plate 2 ave The change in ΔT ave Since there is a proportional relationship between the average press cylinder position G and the cylinder position G, ave The change in ΔG ave and the average thickness T ave The change in ΔT ave The following relationship (Equation 32) holds between them.

[0165] ΔT ave = G × ΔG ave ...(Formula 32) G is the proportionality constant.

[0166] Average thickness T after S seconds from the start of acceleration or deceleration ave The change in ΔT ave,s Average press cylinder position G to zero ave Correction value ΔG ave,s From the above relationships of (Equation 26), (Equation 27), and (Equation 32), ΔV s and ΔT ave can be obtained by removing the above and using the following (Equation 33).

[0167] ΔG ave,s={(D×α) / G}×S (Formula 33) The average press cylinder position during acceleration or deceleration is G ave,0 Then, the average press cylinder position after S seconds is G ave,0 +ΔG ave,s By feedforward controlling the cylinder positions of the first press cylinder 41a and the second press cylinder 42a so that the thickness of the electrode plate 2 changes due to changes in the line speed, it is possible to suppress changes in the thickness of the electrode plate 2 caused by changes in the line speed.

[0168] The driving press cylinder position G during the acceleration or deceleration period of the conveyor line m and the operating side press cylinder position G s The difference between the acceleration period and the deceleration period may basically be the same as before the acceleration or deceleration. Note that if the change in thickness of the electrode plate 2 caused by the change in line speed differs between the driving side and the operating side due to the difference in rigidity between the driving side and the operating side of the roll press device 1, the difference between the acceleration period and the deceleration period may be changed.

[0169] Before the start of acceleration of the transport line, the acceleration start time, the acceleration end time, the line speed V0 at the start of acceleration, and the acceleration α are supplied to the correction value calculation unit 815 from the line speed setting change unit 819. Also, before the start of deceleration of the transport line, the deceleration start time, the deceleration end time, the line speed V0 at the start of deceleration, and the deceleration α are supplied to the correction value calculation unit 815 from the line speed setting change unit 819.

[0170] The correction value calculation unit 815 calculates the change in the line speed S seconds after the start of acceleration, ΔV, based on the line speed V0 at the start of acceleration and the acceleration α, as expressed in (Equation 26) above. s The correction value calculation unit 815 calculates the calculated change amount ΔV s Substituting this into Equation 27 above, the average thickness T after S seconds from the start of acceleration is obtained. ave The change in ΔT ave,s The correction value calculation unit 815 predicts the average thickness T ave The change in ΔT ave,s Average press cylinder position G to zero ave Correction value ΔG ave,s Calculate.

[0171] In the example shown in FIG. 11, the correction value calculation unit 815 calculates the average press cylinder position G ave Correction value ΔG 0.1 , ΔG 0.2 , , ΔG tend Calculate the average press cylinder position G ave Correction value ΔG 0.1 , ΔG 0.2 , , ΔG tend is supplied to the set value correction unit 816.

[0172] The set value correction unit 816 receives the average press cylinder position G ave Correction value ΔG 0.1 , ΔG 0.2 , , ΔG tend The set value correction unit 816 applies a correction value ΔG to the press cylinder position set value G0 at the start of acceleration. 0.1 , ΔG 0.2 , , ΔG tend Add these together to get the corrected press cylinder position setting value G0+ΔG 0.1 , G0+ΔG 02 , , G0+ΔG tend The press cylinder position set value G0 at the start of acceleration is, for example, the press cylinder position set value G input by an operator via the HMI. The set value correcting unit 816 calculates the corrected press cylinder position set value G0+ΔG 0.1 , G0+ΔG 02 , , G0+ΔG tend is supplied to the cylinder position deviation calculation unit 817f.

[0173] The cylinder position deviation calculation unit 817f calculates the corrected press cylinder position setting value G0+ΔG 0.1 , G0+ΔG 02 , , G0+ΔG tendThe cylinder position deviation calculation unit 817f calculates the deviation between the corrected press cylinder position set value G0+ΔG0 supplied from the set value correction unit 816 and the actual cylinder position value of the first press cylinder 41a measured by the first magnet scale 41c at each time. 0.1 , G0+ΔG 02 , , G0+ΔG tend and the actual cylinder position of the second press cylinder 42a measured by the second magnetoscale 42c is calculated at each time.

[0174] The cylinder position deviation calculation unit 817f supplies the calculated cylinder position deviation of the first press cylinder 41a and the cylinder position deviation of the second press cylinder 42a to a PID control unit 817e. The PID control unit 817e generates a manipulated variable for the pressure of the first press cylinder 41a and a manipulated variable for the pressure of the second press cylinder 42a, based on the cylinder position deviation of the first press cylinder 41a and the cylinder position deviation of the second press cylinder 42a.

[0175] The PID control unit 817e supplies the generated manipulated variable for the pressure of the first press cylinder 41a and the manipulated variable for the pressure of the second press cylinder 42a to the cylinder position control unit 817d. The cylinder position control unit 817d includes an actuator, and drives the first press cylinder 41a and the second press cylinder 42a based on the manipulated variable for the pressure of the first press cylinder 41a and the manipulated variable for the pressure of the second press cylinder 42a. Although the above explanation has been given assuming acceleration, the same control is performed during deceleration.

[0176] The delay time from when the cylinder position setting is changed until the actual cylinder position changes (time lag t e ) must be taken into consideration. Therefore, the line speed setting change unit 819 determines the time lag t eA command value for changing the line speed is supplied to the line speed control unit 8110 with a timing delayed by a time corresponding to the change in the line speed. This makes it possible to change the operation of the actuator more appropriately in response to changes in the line speed, and to correct the thickness of the electrode plate 2 with high accuracy. As described above, it is desirable to use a highly responsive hydraulic servo valve for pressure control of the first press cylinder 41a and the second press cylinder 42a.

[0177] In this way, in feedforward control example 2, the change in thickness of the electrode plate 2 due to a change in line speed is predicted, the press cylinder position required to maintain a constant thickness of the electrode plate 2 is calculated, and the press cylinder position is changed by feedforward control. This makes it possible to suppress the change in thickness of the electrode plate 2 during the acceleration or deceleration period of the conveyor line with high accuracy.

[0178] FIG. 12 is a diagram for explaining feedforward control example 3 using the first control panel 81. Feedforward control example 3 is a control used in the roll press apparatus according to embodiment 1 shown in FIG. 1. In feedforward control example 3, a first electric screw 41b and a second electric screw 42b are used as a compression mechanism. Below, differences from feedforward control example 1 shown in FIG. 10 will be described. In feedforward control example 3, a screw position control unit 817g, a PID control unit 817h, and a screw position deviation calculation unit 817i are provided instead of the press pressure control unit 817a, the PID control unit 817b, and the press pressure deviation calculation unit 817c.

[0179] In feedforward control example 3, a sufficiently large pressure (fixed value) is applied to the first press cylinder 41a and the second press cylinder 42a so that the cylinder position does not change due to a change in the position of the first electric screw 41b and the second electric screw 42b. In this state, the press load acting on the electrode plate 2 is changed by changing the positions of the first electric screw 41b and the second electric screw 42b. The positions of the first electric screw 41b and the second electric screw 42b are controlled by a servo motor. Drive side electric screw position D mand the operating side electric screw position D s Average screw position D ave =(D m +D s ) / 2 change ΔD ave and the average thickness T of the electrode plate 2 ave The change in ΔT ave Since there is a proportional relationship between the average screw position D and the screw position D, ave The change in ΔD ave and the average thickness T ave The change in ΔT ave The following relationship (Equation 34) holds between them.

[0180] ΔT ave = H × ΔD ave ...(Formula 34) H is the proportionality constant.

[0181] Average thickness T after S seconds from the start of acceleration or deceleration ave The change in ΔT ave,s Average screw position D to make zero ave Correction value ΔD ave,s From the above relationships of (Equation 26), (Equation 27), and (Equation 34), ΔV s and ΔT ave can be obtained by removing the above and using the following (Equation 35).

[0182] ΔD ave,s ={(D×α) / H}×S (Equation 35) The average screw position during acceleration or deceleration is D ave,0 Then, the average screw position after S seconds is D ave,0 +ΔD ave,s By feedforward controlling the positions of the first electric screw 41b and the second electric screw 42b so that the thickness of the electrode plate 2 changes due to a change in the line speed, it is possible to suppress a change in the thickness of the electrode plate 2 caused by a change in the line speed.

[0183] Position D of the driving electric screw during the acceleration or deceleration period of the conveyor line m and the operating side electric screw position D sThe difference between the acceleration period and the deceleration period may basically be the same as before the acceleration or deceleration. Note that if the change in thickness of the electrode plate 2 caused by the change in line speed differs between the driving side and the operating side due to the difference in rigidity between the driving side and the operating side of the roll press device 1, the difference between the acceleration period and the deceleration period may be changed.

[0184] Before the start of acceleration of the transport line, the acceleration start time, the acceleration end time, the line speed V0 at the start of acceleration, and the acceleration α are supplied to the correction value calculation unit 815 from the line speed setting change unit 819. Also, before the start of deceleration of the transport line, the deceleration start time, the deceleration end time, the line speed V0 at the start of deceleration, and the deceleration α are supplied to the correction value calculation unit 815 from the line speed setting change unit 819.

[0185] The correction value calculation unit 815 calculates the change in the line speed S seconds after the start of acceleration, ΔV, based on the line speed V0 at the start of acceleration and the acceleration α, as expressed in (Equation 26) above. s The correction value calculation unit 815 calculates the calculated change amount ΔV s Substituting this into Equation 27 above, the average thickness T after S seconds from the start of acceleration is obtained. ave The change in ΔT ave,s The correction value calculation unit 815 predicts the average thickness T ave The change in ΔT ave,s Average screw position D to make zero ave Correction value ΔD ave,s Calculate.

[0186] In the example shown in FIG. 12, the correction value calculation unit 815 calculates the average electric screw position D ave Correction value ΔD 0.1 , ΔD 0.2 , , ΔD tend Calculate the average screw position D ave Correction value ΔD 0.1 , ΔD 0.2 , , ΔD tend is supplied to the set value correction unit 816.

[0187] The set value correction unit 816 receives the average electric screw position D aveCorrection value ΔD 0.1 , ΔD 0.2 , , ΔD tend The set value correction unit 816 applies a correction value ΔD to the electric screw position set value D0 at the start of acceleration. 0.1 , ΔD 0.2 , , ΔD tend Add these together to get the corrected electric screw position setting value D0+ΔD 0.1 , D0+ΔD 02 , , D0+ΔD tend The electric screw position set value D0 at the start of acceleration is, for example, the electric screw position set value D input by an operator via the HMI. The set value correcting unit 816 calculates the corrected electric screw position set value D0+ΔD 0.1 , D0+ΔD 02 , , D0+ΔD tend is supplied to the screw position deviation calculation unit 817i.

[0188] The screw position deviation calculation unit 817i calculates the corrected electric screw position set value D0+ΔD supplied from the set value correction unit 816. 0.1 , D0+ΔD 02 , , D0+ΔD tend The screw position deviation calculation unit 817i calculates the deviation between the measured value of the position of the first electric screw 41b and the corrected electric screw position set value D0+ΔD 0.1 , D0+ΔD 02 , , D0+ΔD tend and the deviation between the measured value of the position of the second electric screw 42b at each time is calculated.

[0189] The screw position control section 817g includes servo motors for pressing down the first electric screw 41b and the second electric screw 42b. The amount of change in the positions of the first electric screw 41b and the second electric screw 42b can be calculated from the rotation speed of each servo motor.

[0190] The screw position deviation calculation unit 817i supplies the calculated position deviation of the first electric screw 41b and the position deviation of the second electric screw 42b to a PID control unit 817h. The PID control unit 817h generates an operation amount for the rotation of the servo motor for the first electric screw 41b and an operation amount for the rotation of the servo motor for the second electric screw 42b based on the position deviation of the first electric screw 41b and the position deviation of the second electric screw 42b.

[0191] The PID control unit 817h supplies the generated manipulated variable of the rotation of the servo motor for the first electric screw 41b and the manipulated variable of the rotation of the servo motor for the second electric screw 42b to the screw position control unit 817g. The screw position control unit 817g drives the servo motor for the first electric screw 41b and the servo motor for the second electric screw 42b based on the manipulated variable of the rotation of the servo motor for the first electric screw 41b and the manipulated variable of the rotation of the servo motor for the second electric screw 42b. Although the above description has been given assuming acceleration, the same control is performed during deceleration.

[0192] The delay time from when the electric screw position setting is changed until the actual electric screw position changes (time lag t e ) must be taken into consideration. Therefore, the line speed setting change unit 819 determines the time lag t e A command value for changing the line speed is supplied to the line speed control unit 8110 at a timing delayed by a time corresponding to the change in the line speed. This makes it possible to change the operation of the servo motor more appropriately in response to the change in the line speed, and to correct the thickness of the electrode plate 2 with high accuracy.

[0193] In this way, in feedforward control example 3, the change in thickness of the electrode plate 2 due to a change in line speed is predicted, the electric screw position required to maintain a constant thickness of the electrode plate 2 is calculated, and the electric screw position is changed by feedforward control. This makes it possible to suppress the change in thickness of the electrode plate 2 during the acceleration or deceleration period of the conveyor line with high accuracy.

[0194] As described above, according to the feedback control examples 1 to 4 using the roll press apparatus 1 according to the first to third embodiments, the driving side thickness measurement value T m , the central thickness measurement T c , the measured thickness on the operating side T s , and the thickness target value T t Based on this, the first feature T t-m , the second feature T t-s , and the third feature T drop Calculate the first feature T t-m , the second feature T t-s , and the third feature T drop The compression mechanism and / or the bending mechanism are controlled so that all of the thicknesses of the electrode plate 2 after compression are zero. A press mechanism or a cotter mechanism can be used as the compression mechanism. This allows the thickness of the electrode plate 2 after compression to be adjusted to the target value T t can be converged to.

[0195] The above-mentioned Patent Document 1 (JP Patent Publication 2013-111647 A) discloses a method of measuring the thickness after compression at three locations, the operation side, the center, and the drive side, and controlling the press mechanism and the bend mechanism so that the difference between the measured thickness and the target thickness falls within a preset threshold value if the difference falls outside the threshold value. In this method, film thickness control is not activated until the threshold value is exceeded, so it is not possible to obtain thickness accuracy equal to or greater than the threshold value, and it may take a long time to converge to the target thickness, or it may not be possible to converge to the target thickness at all.

[0196] In the above method, the driving side thickness, the operating side thickness, and the target thickness are compared, and if at least one of the driving side thickness and the operating side thickness exceeds a threshold value, the position of the press cylinder is reset to correct this, and the pressure of the bend cylinder is calculated and set to maintain the deflection correction amount that changes due to the change in the position of the press cylinder. If both the driving side thickness and the operating side thickness do not exceed the threshold value, the central thickness is compared with the threshold value, and if it exceeds the threshold value, it is determined that the roll deformation in the central portion has become large, so only the pressure of the bend cylinder is changed and the position of the press cylinder is not changed. These control flows are executed repeatedly.

[0197] Generally, the pressure change of the bending cylinder acts in the direction of opening the roll gap, and changes the rolling load on the rolled material, which is accompanied by a change in thickness. Therefore, in any of the steps in the above control flow, the film thickness changes due to the change in the pressure of the bending cylinder, and the thickness again deviates from the threshold value, so that it takes time to reach the target thickness or there are cases where the thickness cannot be controlled to the threshold value. In particular, the narrower the threshold value is, or the greater the need to change the position of the press cylinder or the pressure of the bending cylinder, the greater the possibility of the thickness again deviating from the threshold value, so there are limitations to the thickness range and control speed that can be controlled.

[0198] As described above, the driving side thickness, the operating side thickness, and the target thickness are compared, and if neither the driving side thickness nor the operating side thickness exceeds the threshold, the central thickness is compared with the threshold, and if the threshold is exceeded, it is determined that the roll deflection is large, and only the pressure of the bending cylinder is changed. In this case, the thicknesses at both ends are controlled to be equal to or less than the threshold before the central thickness is controlled, so it takes time to converge to the target thickness. Furthermore, in the process of controlling the thicknesses at both ends, the central thickness may deviate from the target thickness. For example, if the central thickness is thicker than the target thickness and the thicknesses at both ends are each thinner than the target thickness, the loads on both sides are controlled to be lowered so that the thicknesses at both ends become the target thickness, but the pressure from the press roll acting on the center of the electrode plate also decreases, so the central thickness becomes thicker and deviates from the target value.

[0199] In contrast, according to feedback control examples 1 to 4 using the roll press apparatus 1 according to the first to third embodiments, the magnitude and direction of the roll deflection are calculated based on the difference between the center thickness and the average thickness at both ends (the third feature value T drop ) and controls the thickness at both ends while simultaneously controlling the thickness difference between the center and both ends due to roll deflection. This makes it possible to converge the thickness of the electrode plate 2 to the target value over the entire width more quickly without worsening the thickness in the width direction.

[0200] In this way, according to the feedback control examples 1 to 4 using the roll press device 1 according to the embodiments 1 to 3, the thickness of the electrode plate 2 after compression is always the target value T t The thickness of the electrode plate 2 is always maintained in a good state by performing feedback control so that the thickness of the electrode plate 2 converges to the target value T t Since the thickness is controlled by the micrometer, there is no need for an operator to periodically stop the line, measure the thickness of the electrode plate 2 with a micrometer, and adjust the pressure value of the compression mechanism and / or the bending mechanism based on the measured value. Therefore, there is no need to assign skilled operators, which makes it possible to reduce labor costs. Also, it is possible to reduce quality variations due to operators.

[0201] In addition, according to the feedback control examples 1 to 4 using the roll press device 1 according to the first to third embodiments, in order to prevent a new correction of the set value from being performed based on the thickness measurement value before the correction of the set value is reflected, after the correction of the set value is performed, the pass line length L from the press position to the thickness meter 70 is t The time t until the length of the electrode plate 2 reaches and the correction of the set value is reflected in the thickness measurement value d After the time has elapsed, the thickness measurement value is acquired. Three feature values ​​are calculated based on the acquired thickness measurement value, and a correction value is calculated based on the three feature values, and the next setting value change is performed.

[0202] In the coating process and drying process before pressing, the thickness of the rolled material after pressing may change due to changes in the coating thickness and hardness of the rolled material, or due to the thermal effects of the pressure roller and main bearings. Even in such cases, by repeatedly and continuously performing the above control, the thickness of the rolled material after pressing can be adjusted to the target value T over the entire width immediately after the thickness gauge 70 detects a thickness change. t Since the thickness can be controlled to be within a certain range, a good thickness can be obtained over the entire length.

[0203] Furthermore, by combining the feedforward control examples 1 to 3, it is possible to suppress with high precision the change in thickness of the electrode plate 2 when the conveyor line accelerates or decelerates. That is, by predicting the change in thickness of the electrode plate 2 due to the change in line speed, calculating the compression conditions for making the predicted change in thickness zero, and feedforward controlling the compression mechanism, it is possible to suppress with high precision the change in thickness due to the change in line speed.

[0204] Since the proportionality constants mentioned above differ depending on the type of material being rolled, it is desirable to measure the proportionality constant for each type.

[0205] The present disclosure has been described above based on the embodiments. The embodiments are merely examples, and it will be understood by those skilled in the art that various modifications are possible in the combination of each component and each processing step, and that such modifications are also within the scope of the present disclosure.

[0206] In Figure 3, an example has been described in which the control device 80 is configured with two control panels, a first control panel 81 and a second control panel 82, but the first control panel 81 and the second control panel 82 may also be integrated into a single control panel.

[0207] In the above-described first to third embodiments, the first feature amount T t-m , the second feature T t-s , and the third feature T drop In the above example, the compression mechanism and / or the bending mechanism are controlled so that all of the third feature quantity T drop is zero, and the thickness measurement value T m and the measured thickness on the operating side T s When the difference between the thickness and the center is zero, the electrode plate 2 is flat in the width direction. drop The compression mechanism and / or the bending mechanism are controlled so that the thickness difference between the edge and the center becomes a negative value. In addition, when manufacturing an electrode plate 2 in which both edges are thinner than the center, the third feature amount T drop The compression mechanism and / or the bending mechanism are controlled so that becomes a positive value according to the thickness difference between the edge and the center.

[0208] That is, by arbitrarily setting β, γ, and δ in the following (Equations 35) to (Equation 37), it is possible to manufacture an electrode plate 2 having an arbitrary thickness profile.

[0209] T t-m +β=0 (Formula 35) T t-s +γ=0 (Formula 36) T drop +δ=0 (Formula 37) β, γ, and δ are arbitrary real numbers [μm].

[0210] In the above-described first to third embodiments, the third feature quantity indicating the second-order component of the thickness profile of the electrode plate is the central thickness measurement value T c and the measured thickness on the driving side T m and the measured thickness on the operating side T s The third feature amount is defined as the difference between the average value of the thickness measured at three or more points and the average value of the thickness measured at three or more points. In this regard, the third feature amount can also be defined from a quadratic or quartic approximation curve derived by using the least squares method based on the thickness measured at three or more points. When approximation is performed using a quadratic curve, the feature amount calculation unit 814 sets the quadratic coefficient of the approximated quadratic curve as the third feature amount. When approximation is performed using a quartic curve, the feature amount calculation unit 814 sets the quadratic coefficient of the approximated quartic curve as the third feature amount. In general, the more sample points there are, the higher the approximation accuracy becomes. In addition, if the function is quadratic or higher, the quadratic coefficient can be derived.

[0211] When five or more thickness measurement points are obtained, the first feature T t-m is the thickness target value T t and the thickness measurement value T of the most driven point among the five or more points. m The second feature T t-s is the thickness target value T t and the thickness measurement value T of the most operated point among the five or more points. s It is defined as the deviation from

[0212] The embodiment may be specified by the following items.

[0213] [Item 1] a first pressure roller (11) and a second pressure roller (12) for pressing and compressing the electrode plates (2) of the secondary batteries which are continuously conveyed; a first main bearing portion (21) and a second main bearing portion (22) provided on one side and the other side of a rotation shaft of the first pressure roller (11), respectively, for rotatably supporting the rotation shaft; a third main bearing portion (23) provided on one side and the other side of the rotation shaft of the second pressure roller (12) for rotatably supporting the rotation shaft; 4 Main bearing ( 24 )and, a first bend bearing portion (31) and a second bend bearing portion (32) provided on one side and the other side of a rotation shaft of the first pressure roller (11), respectively, for rotatably supporting the rotation shaft; a third bend bearing portion (33) and a fourth bend bearing portion (34) provided on one side and the other side of a rotation shaft of the second pressure roller (12), respectively, for rotatably supporting the rotation shaft; a first compression mechanism (41) capable of applying a load to at least one of the first main bearing portion (21) and the third main bearing portion (23) in a direction in which the first pressure roller (11) and the second pressure roller (12) approach each other; The second main bearing portion (22) and the 4 Main bearing ( 24 a second compression mechanism (42) capable of applying a load to at least one of the first and second pressure rollers (11, 12) in a direction in which the first and second pressure rollers (11, 12) approach each other; a first bend mechanism (51) capable of applying a load to at least one of the first bend bearing portion (31) and the third bend bearing portion (33) in a direction in which the first pressure roller (11) and the second pressure roller (12) come into contact with and separate from each other; a second bend mechanism (52) capable of applying a load to at least one of the second bend bearing portion (32) and the fourth bend bearing portion (34) in a direction in which the first pressure roller (11) and the second pressure roller (12) move toward and away from each other; a thickness meter (70) provided on the exit side of the first pressure roller (11) and the second pressure roller (12) for detecting the thickness of the electrode plate (2) of the secondary battery at three or more points in the width direction of the electrode plate (2); calculation units (814 to 816) that calculate setting values ​​for each of the first compression mechanism (41), the second compression mechanism (42), the first bending mechanism (51), and the second bending mechanism (52) based on three or more thickness measurement values ​​based on the detection values ​​of the thickness meter (70) and a target thickness value; and control units (817, 818) configured to control loads of the first compression mechanism (41), the second compression mechanism (42), the first bend mechanism (51), and the second bend mechanism (52), based on the set values ​​calculated by the calculation units (814 to 816), the calculation units (814 to 816) calculate three feature amounts: a first deviation between a target thickness value and a thickness measurement value of a point among the three or more points that is closest to the first compression mechanism (41), a second deviation between the target thickness value and a thickness measurement value of a point among the three or more points that is closest to the second compression mechanism (42), and a second component of a thickness profile of the electrode plate (2), and adaptively change setting values ​​of the first compression mechanism (41), the second compression mechanism (42), the first bend mechanism (51), and the second bend mechanism (52) based on the three feature amounts. Roll press equipment (1).

[0214] This allows the roll press device (1) to control the thickness of the electrode plate (2) with high precision.

[0215] [Item 2] the thickness meter (70) is provided on the exit side of the first pressure roller (11) and the second pressure roller (12) and detects the thickness of the electrode plate (2) of the secondary battery at a first point, a second point, and a third point aligned in the width direction of the electrode plate (2), the calculation units (814 to 816) calculate setting values ​​of the first compression mechanism (41), the second compression mechanism (42), the first bending mechanism (51), and the second bending mechanism (52) based on a first point thickness measurement value, a second point thickness measurement value, and a third point thickness measurement value based on the detection value of the thickness meter (70) and a target thickness value, the first point is set at an end of an electrode plate (2) of the secondary battery on a side where the first compression mechanism (41) is provided, The second point is set at the center of the electrode plate (2) of the secondary battery, the third point is set at an end of an electrode plate (2) of the secondary battery on a side where the second compression mechanism (42) is provided, The calculation unit (814 to 816) calculates a first deviation between the first point thickness measurement value and the thickness target value, 3 Calculating three feature quantities: a second deviation between the measured thickness value and the target thickness value, and a second-order component of the thickness profile of the electrode plate (2); The secondary component of the thickness profile of the electrode plate (2) is defined as the difference between the second point thickness measurement value and the average value of the first point thickness measurement value and the third point thickness measurement value. The roll press apparatus (1) according to item 1.

[0216] According to this, the thickness in the width direction of the electrode plate (2) can be profiled with high accuracy by three feature amounts calculated from the thickness measurement values ​​at three points.

[0217] [Item 3] the calculation units (814 to 816) calculate setting values ​​of the first compression mechanism (41), the second compression mechanism (42), the first bend mechanism (51), and the second bend mechanism (52), respectively, based on a relationship between the loads generated by the first compression mechanism (41), the second compression mechanism (42), the first bend mechanism (51), and the second bend mechanism (52) and the three feature amounts, the relationship being derived in advance, so that all of the three feature amounts become zero. 3. The roll press apparatus (1) according to item 1 or 2.

[0218] According to this, the change in thickness of the electrode plate (2) can be suppressed with high accuracy by feedback control using the three feature amounts.

[0219] [Item 4] The first compression mechanism (41) includes a cylinder (41a) for a first press, The second compression mechanism (42) includes a cylinder (42a) for a second press, The first bending mechanism (51) includes a cylinder (51a or 51b, 51c) for a first bend, The second bending mechanism (52) includes a cylinder (52a or 52b, 52c) for a second bend, the calculation units (814 to 816) calculate set values ​​for the pressure of the cylinder (41a) for the first press, the pressure of the cylinder (42a) for the second press, the pressure of the cylinder (51a or 51b, 51c) for the first bend, and the pressure of the cylinder (52a or 52b, 52c) for the second bend, so that all of the three feature amounts become zero. Item 3. The roll press apparatus (1) according to item 3.

[0220] According to this, by using the three feature quantities to feedback-control the pressure of the cylinder (41a) for the first press, the pressure of the cylinder (42a) for the second press, the pressure of the cylinder (51a or 51b, 51c) for the first bend, and the pressure of the cylinder (52a or 52b, 52c) for the second bend, it is possible to suppress the change in thickness of the electrode plate (2) with high precision.

[0221] [Item 5] The first compression mechanism (41) includes a cylinder (41a) for a first press, The second compression mechanism (42) includes a cylinder (42a) for a second press, The first bending mechanism (51) includes a cylinder (51a or 51b, 51c) for a first bend, The second bending mechanism (52) includes a cylinder (52a or 52b, 52c) for a second bend, the calculation units (814 to 816) calculate set values ​​for the position of the first press cylinder (41a), the position of the second press cylinder (42a), the pressure of the first bend cylinder (51a or 51b, 51c), and the pressure of the second bend cylinder (52a or 52b, 52c) so that all of the three feature amounts become zero. Item 3. The roll press apparatus (1) according to item 3.

[0222] According to this, by using the three feature amounts to feedback control the position of the cylinder for the first press (41a), the position of the cylinder for the second press (42a), the pressure of the cylinder for the first bend (51a or 51b, 51c), and the pressure of the cylinder for the second bend (52a or 52b, 52c), it is possible to suppress the change in thickness of the electrode plate (2) with high precision.

[0223] [Item 6] the first compression mechanism (41) further includes a first magnetoscale (41c) for measuring a position of the cylinder (41a) for the first press, the second compression mechanism (42) further includes a second magnet scale (42c) for measuring a position of the cylinder (42a) for the second press, The control unit (817d, 818) controlling a pressure of the cylinder (41a) for the first press so that a position of the cylinder (41a) for the first press measured by the first magnetoscale (41c) coincides with a position of the cylinder (41a) for the first press supplied from the calculation units (814 to 816); controlling the pressure of the cylinder (42a) for the second press so that the position of the cylinder (42a) for the second press measured by the second magnet scale (42c) coincides with the position of the cylinder (42a) for the second press supplied from the calculation units (814 to 816); Item 6. The roll press apparatus (1) according to item 5.

[0224] According to this, the position of the cylinder (41 a) for the first press and the position of the cylinder (42 a) for the second press can be measured with high accuracy using the first magnetic scale (41 c) and the second magnetic scale (42 c), thereby realizing feedback control of the compression mechanism with high responsiveness.

[0225] [Item 7] The first compression mechanism (41) includes a first electric screw (41b), the second compression mechanism (42) includes a second electric screw (42b), The first bending mechanism (51) includes a cylinder (51a or 51b, 51c) for a first bend, The second bending mechanism (52) includes a cylinder (52a or 52b, 52c) for a second bend, the calculation units (814 to 816) calculate set values ​​for the position of the first electric screw (41b), the position of the second electric screw (42b), the pressure of the cylinder (51a or 51b, 51c) for the first bend, and the pressure of the cylinder (52a or 52b, 52c) for the second bend, so that all of the three feature amounts become zero. Item 3. The roll press apparatus (1) according to item 3.

[0226] According to this, by using the three feature quantities to feedback control the position of the first electric screw (41b), the position of the second electric screw (42b), the pressure of the cylinder for the first bend (51a or 51b, 51c), and the pressure of the cylinder for the second bend (52a or 52b, 52c), it is possible to suppress the change in thickness of the electrode plate (2) with high precision.

[0227] [Item 8] The first compression mechanism (41) includes a first electric cotter (41e), The second compression mechanism (42) includes a second electric cotter (42e), The first bending mechanism (51) includes a cylinder (51a or 51b, 51c) for a first bend, The second bending mechanism (52) includes a cylinder (52a or 52b, 52c) for a second bend, The calculation units (814 to 816) calculate set values ​​for the height of the first electric cotter (41e), the height of the second electric cotter (42e), the pressure of the cylinder for the first bend (51a or 51b, 51c), and the pressure of the cylinder for the second bend (52a or 52b, 52c) so that all of the three feature amounts become zero. Item 3. The roll press apparatus (1) according to item 3.

[0228] According to this, by using the three feature quantities to feedback control the height of the first electric cotter (41e), the height of the second electric cotter (42e), the pressure of the cylinder for the first bend (51a or 51b, 51c), and the pressure of the cylinder for the second bend (52a or 52b, 52c), it is possible to suppress the change in thickness of the electrode plate (2) with high precision.

[0229] [Item 9] The thickness meter (70) scans one thickness detection sensor in the width direction of the electrode plate (2) to continuously detect the thickness of the electrode plate (2), and extracts thickness detection values ​​at the three or more points. The roll press apparatus (1) according to any one of items 1 to 8.

[0230] This allows the number of thickness detection sensors to be reduced.

[0231] [Item 10] The thickness meter (70) detects the thickness at the three or more points using three or more thickness detection sensors, The roll press apparatus (1) according to any one of items 1 to 8.

[0232] This makes it possible to simplify the control of each thickness detection sensor.

[0233] [Item 11] The thickness measurement value calculation unit (821) further includes a thickness measurement value calculation unit that calculates thickness measurement values ​​of the three or more points by filtering the three or more thickness detection values ​​detected by the thickness meter (70) in the longitudinal direction of the electrode plate (2). The roll press apparatus (1) according to item 9 or 10.

[0234] This makes it possible to remove noise from the detection value.

[0235] [Item 12] After changing the setting values ​​of the first compression mechanism (41), the second compression mechanism (42), the first bend mechanism (51), and the second bend mechanism (52), the calculation units (814 to 816) reserve the right to make a next change to the setting values ​​of the first compression mechanism (41), the second compression mechanism (42), the first bend mechanism (51), and the second bend mechanism (52) until a predetermined condition is satisfied regarding a pass line length from a press position to the thickness meter (70) and a time until the change in the setting values ​​is reflected in an actual output. The roll press apparatus (1) according to any one of items 1 to 8.

[0236] This makes it possible to avoid unnecessary or excessive changes to the settings of the compression mechanism and / or the bend mechanism.

[0237] [Item 13] a first pressure roller (11) and a second pressure roller (12) for pressing and compressing the electrode plates (2) of the secondary batteries which are continuously conveyed; a first main bearing portion (21) and a second main bearing portion (22) provided on one side and the other side of a rotation shaft of the first pressure roller (11), respectively, for rotatably supporting the rotation shaft; a third main bearing portion (23) and a fourth main bearing portion (24) provided on one side and the other side of the rotation shaft of the second pressure roller (12) for rotatably supporting the rotation shaft; main Bearing part ( 24 )and, a first bend bearing portion (31) and a second bend bearing portion (32) provided on one side and the other side of a rotation shaft of the first pressure roller (11), respectively, for rotatably supporting the rotation shaft; a third bend bearing portion (33) and a fourth bend bearing portion (34) provided on one side and the other side of a rotation shaft of the second pressure roller (12), respectively, for rotatably supporting the rotation shaft; a first compression mechanism (41) capable of applying a load to at least one of the first main bearing portion (21) and the third main bearing portion (23) in a direction in which the first pressure roller (11) and the second pressure roller (12) approach each other; The second main bearing portion (22) and the fourth main bearing portion (23) main Bearing part ( 24 a second compression mechanism (42) capable of applying a load to at least one of the first and second pressure rollers (11, 12) in a direction in which the first and second pressure rollers (11, 12) approach each other; a first bend mechanism (51) capable of applying a load to at least one of the first bend bearing portion (31) and the third bend bearing portion (33) in a direction in which the first pressure roller (11) and the second pressure roller (12) come into contact with and separate from each other; a second bend mechanism (52) capable of applying a load to at least one of the second bend bearing portion (32) and the fourth bend bearing portion (34) in a direction in which the first pressure roller (11) and the second pressure roller (12) move toward and away from each other; a thickness meter (70) provided on the exit side of the first pressure roller (11) and the second pressure roller (12) for detecting the thickness of the electrode plate (2) of the secondary battery at three or more points in the width direction of the electrode plate (2); A control device (80) for use in a roll press device (1) comprising: calculation units (814 to 816) that calculate setting values ​​for each of the first compression mechanism (41), the second compression mechanism (42), the first bending mechanism (51), and the second bending mechanism (52) based on three or more thickness measurement values ​​based on the detection values ​​of the thickness meter (70) and a target thickness value; and control units (817, 818) configured to control loads of the first compression mechanism (41), the second compression mechanism (42), the first bend mechanism (51), and the second bend mechanism (52), based on the set values ​​calculated by the calculation units (814 to 816), the calculation units (814 to 816) calculate three feature amounts: a first deviation between a target thickness value and a thickness measurement value of a point among the three or more points that is closest to the first compression mechanism (41), a second deviation between the target thickness value and a thickness measurement value of a point among the three or more points that is closest to the second compression mechanism (42), and a second component of a thickness profile of the electrode plate (2), and adaptively change setting values ​​of the first compression mechanism (41), the second compression mechanism (42), the first bend mechanism (51), and the second bend mechanism (52) based on the three feature amounts. A control device (80).

[0238] This allows the roll press device (1) to control the thickness of the electrode plate (2) with high precision. [Explanation of symbols]

[0239] 1 Roll press device 2 Electrode plate 11 First pressure roller 12 Second pressure roller 13 Unwinding machine 14 Winder 15 Motor 16 Pulse Generator 21~24 Main bearing part 31~34 Bend bearing section 41 First compression mechanism 42 Second compression mechanism 41a First press cylinder 41b First electric screw 41c 1st Magnescale 41d First load cell 41e First electric cotter 42a Second press cylinder 42b Second electric screw 42c 2nd Magnescale 42d Second load cell 42e 2nd electric cotter 51 First bending mechanism 51a First bend cylinder 51b 3rd bend cylinder 51c 5th bend cylinder 52a Second bend cylinder 52b 4th bend cylinder 52c 6th bend cylinder 52 Second bending mechanism 61 First preload mechanism 61a First preload cylinder 62 Second preload mechanism 62a Second preload cylinder 70 Thickness Gauge 80 Control device 81 First control panel 811 Length measurement unit 812 Acquisition timing generation unit 813 Thickness measurement acquisition unit 814 Feature Calculation Unit 815 Correction value calculation unit 816 Setting value correction unit 817a Press pressure control section 817b PID control unit 817c Press pressure deviation calculation part 817d Cylinder position control unit 817e PID control unit 817f Cylinder position deviation calculation part 817g Screw position control unit 817h PID control unit 817i Screw position deviation calculation unit 817j Cotter height control section 817k PID control unit 817l Cotter height deviation calculation unit 818a Bend pressure control section 818b PID control unit 818c Bend pressure deviation calculation section 819 Line speed setting change unit 8110 Line speed control section.

Claims

1. a first pressure roller and a second pressure roller for pressing and compressing the electrode plates of the secondary batteries which are continuously conveyed; a first main bearing portion and a second main bearing portion provided on one side and the other side of a rotation shaft of the first pressure roller, respectively, for rotatably supporting the rotation shaft; a third main bearing portion and a fourth main bearing portion provided on one side and the other side of a rotation shaft of the second pressure roller, respectively, for rotatably supporting the rotation shaft; a first bend bearing portion and a second bend bearing portion provided on one side and the other side of a rotation shaft of the first pressure roller, respectively, for rotatably supporting the rotation shaft; a third bend bearing portion and a fourth bend bearing portion provided on one side and the other side of a rotation shaft of the second pressure roller, respectively, for rotatably supporting the rotation shaft; a first compression mechanism capable of applying a load to at least one of the first main bearing portion and the third main bearing portion in a direction in which the first pressure roller and the second pressure roller approach each other; a second compression mechanism capable of applying a load to at least one of the second main bearing portion and the fourth main bearing portion in a direction in which the first pressure roller and the second pressure roller approach each other; a first bend mechanism capable of applying a load to at least one of the first bend bearing portion and the third bend bearing portion in a direction in which the first pressure roller and the second pressure roller separate from each other; a second bend mechanism capable of applying a load to at least one of the second bend bearing portion and the fourth bend bearing portion in a direction in which the first pressure roller and the second pressure roller separate from each other; a thickness meter provided on the exit side of the first pressure roller and the second pressure roller, the thickness meter detecting the thickness of the electrode plate of the secondary battery at three or more points in a width direction of the electrode plate; a calculation unit that calculates setting values ​​of the first compression mechanism, the second compression mechanism, the first bending mechanism, and the second bending mechanism based on three or more thickness measurement values ​​based on the detection values ​​of the thickness meter and a thickness target value; a control unit that controls loads of the first compression mechanism, the second compression mechanism, the first bending mechanism, and the second bending mechanism based on the set values ​​calculated by the calculation unit, the calculation unit calculates three feature amounts: a first deviation between a thickness target value and a thickness measurement value of a point among the three or more points that is closest to the first compression mechanism, a second deviation between the thickness target value and a thickness measurement value of a point among the three or more points that is closest to the second compression mechanism, and a second component of a thickness profile of the electrode plate, and adaptively changes setting values ​​of the first compression mechanism, the second compression mechanism, the first bend mechanism, and the second bend mechanism based on the three feature amounts; After changing the setting values ​​of the first compression mechanism, the second compression mechanism, the first bend mechanism, and the second bend mechanism, the calculation unit reserves the right to change the setting values ​​of the first compression mechanism, the second compression mechanism, the first bend mechanism, and the second bend mechanism until a predetermined condition is satisfied regarding a path line length from a press position to the thickness meter and a time until the change in the setting values ​​is reflected in an actual output. Roll press equipment.

2. the thickness meter is provided on the exit side of the first pressure roller and the second pressure roller, and detects the thickness of the electrode plate of the secondary battery at a first point, a second point, and a third point aligned in a width direction of the electrode plate, respectively; the calculation unit calculates setting values ​​of the first compression mechanism, the second compression mechanism, the first bending mechanism, and the second bending mechanism based on a first point thickness measurement value, a second point thickness measurement value, and a third point thickness measurement value based on the detection value of the thickness meter and the thickness target value; the first point is set at an end of an electrode plate of the secondary battery on a side where the first compression mechanism is provided, The second point is set at a center of an electrode plate of the secondary battery, the third point is set at an end of an electrode plate of the secondary battery on a side where the second compression mechanism is provided, the calculation unit calculates three feature amounts, a first deviation between the first point thickness measurement value and the thickness target value, a second deviation between the third point thickness measurement value and the thickness target value, and a second-order component of a thickness profile of the electrode plate, from the first point thickness measurement value, the second point thickness measurement value, the third point thickness measurement value, and the thickness target value; a second order component of the thickness profile of the electrode plate is defined as a difference between the second point thickness measurement and an average of the first point thickness measurement and the third point thickness measurement; The roll press apparatus according to claim 1 .

3. the calculation unit calculates setting values ​​of the first compression mechanism, the second compression mechanism, the first bend mechanism, and the second bend mechanism, based on a relationship between the loads generated by the first compression mechanism, the second compression mechanism, the first bend mechanism, and the second bend mechanism and the three feature amounts, so that all of the three feature amounts become zero. The roll press apparatus according to claim 1 or 2.

4. the first compression mechanism includes a cylinder for a first press, the second compression mechanism includes a cylinder for a second press, the first bending mechanism includes a cylinder for a first bend, the second bending mechanism includes a cylinder for a second bend, the calculation unit calculates set values ​​for each of the pressure of the cylinder for the first press, the pressure of the cylinder for the second press, the pressure of the cylinder for the first bend, and the pressure of the cylinder for the second bend, so that all of the three feature quantities become zero. The roll press apparatus according to claim 3 .

5. the first compression mechanism includes a cylinder for a first press, the second compression mechanism includes a cylinder for a second press, the first bending mechanism includes a cylinder for a first bend, the second bending mechanism includes a cylinder for a second bend, the calculation unit calculates set values ​​for a position of the cylinder for the first press, a position of the cylinder for the second press, a pressure of the cylinder for the first bend, and a pressure of the cylinder for the second bend, so that all of the three feature amounts become zero. The roll press apparatus according to claim 3 .

6. the first compression mechanism further includes a first magnetoscale for measuring a position of a cylinder for the first press; the second compression mechanism further includes a second magnet scale for measuring a position of a cylinder for the second press, The control unit is controlling a pressure of the cylinder for the first press so that a position of the cylinder for the first press measured by the first magnetoscale coincides with a position of the cylinder for the first press supplied from the calculation unit; controlling a pressure of the cylinder for the second press so that a position of the cylinder for the second press measured by the second magnet scale coincides with a position of the cylinder for the second press supplied from the calculation unit; The roll press apparatus according to claim 5 .

7. the first compression mechanism includes a first electric screw, the second compression mechanism includes a second electric screw, the first bending mechanism includes a cylinder for a first bend, the second bending mechanism includes a cylinder for a second bend, the calculation unit calculates set values ​​of the position of the first electric screw, the position of the second electric screw, the pressure of the cylinder for the first bend, and the pressure of the cylinder for the second bend so that all of the three feature amounts become zero. The roll press apparatus according to claim 3 .

8. the first compression mechanism includes a first motor-driven cotter; the second compression mechanism includes a second motor-driven cotter; the first bending mechanism includes a cylinder for a first bend, the second bending mechanism includes a cylinder for a second bend, the calculation unit calculates set values ​​for the height of the first electric cotter, the height of the second electric cotter, the pressure of the cylinder for the first bend, and the pressure of the cylinder for the second bend so that all of the three feature amounts become zero. The roll press apparatus according to claim 3 .

9. The thickness meter is configured to continuously detect the thickness of the electrode plate by scanning one thickness detection sensor in the width direction of the electrode plate, and extract the thickness detection values ​​at the three or more points. The roll press apparatus according to any one of claims 1 to 8.

10. The thickness meter detects the thicknesses at the three or more points using three or more thickness detection sensors. The roll press apparatus according to any one of claims 1 to 8.

11. A thickness measurement value calculation unit is further provided which filters three or more thickness detection values ​​detected by the thickness meter in the longitudinal direction of the electrode plate to calculate thickness measurement values ​​of the three or more points. The roll press apparatus according to claim 9 or 10.

12. a first pressure roller and a second pressure roller for pressing and compressing the electrode plates of the secondary batteries which are continuously conveyed; a first main bearing portion and a second main bearing portion provided on one side and the other side of a rotation shaft of the first pressure roller, respectively, for rotatably supporting the rotation shaft; a third main bearing portion and a fourth main bearing portion provided on one side and the other side of a rotation shaft of the second pressure roller, respectively, for rotatably supporting the rotation shaft; a first bend bearing portion and a second bend bearing portion provided on one side and the other side of a rotation shaft of the first pressure roller, respectively, for rotatably supporting the rotation shaft; a third bend bearing portion and a fourth bend bearing portion provided on one side and the other side of a rotation shaft of the second pressure roller, respectively, for rotatably supporting the rotation shaft; a first compression mechanism capable of applying a load to at least one of the first main bearing portion and the third main bearing portion in a direction in which the first pressure roller and the second pressure roller approach each other; a second compression mechanism capable of applying a load to at least one of the second main bearing portion and the fourth main bearing portion in a direction in which the first pressure roller and the second pressure roller approach each other; a first bend mechanism capable of applying a load to at least one of the first bend bearing portion and the third bend bearing portion in a direction in which the first pressure roller and the second pressure roller separate from each other; a second bend mechanism capable of applying a load to at least one of the second bend bearing portion and the fourth bend bearing portion in a direction in which the first pressure roller and the second pressure roller separate from each other; a thickness meter provided on the exit side of the first pressure roller and the second pressure roller, the thickness meter detecting the thickness of the electrode plate of the secondary battery at three or more points in a width direction of the electrode plate; A control device for use in a roll press device comprising: a calculation unit that calculates setting values ​​of the first compression mechanism, the second compression mechanism, the first bending mechanism, and the second bending mechanism based on three or more thickness measurement values ​​based on the detection values ​​of the thickness meter and a thickness target value; a control unit that controls loads of the first compression mechanism, the second compression mechanism, the first bending mechanism, and the second bending mechanism based on the set values ​​calculated by the calculation unit, the calculation unit calculates three feature amounts: a first deviation between a thickness target value and a thickness measurement value of a point among the three or more points that is closest to the first compression mechanism, a second deviation between the thickness target value and a thickness measurement value of a point among the three or more points that is closest to the second compression mechanism, and a second component of a thickness profile of the electrode plate, and adaptively changes setting values ​​of the first compression mechanism, the second compression mechanism, the first bend mechanism, and the second bend mechanism based on the three feature amounts; After changing the setting values ​​of the first compression mechanism, the second compression mechanism, the first bend mechanism, and the second bend mechanism, the calculation unit reserves the right to change the setting values ​​of the first compression mechanism, the second compression mechanism, the first bend mechanism, and the second bend mechanism until a predetermined condition is satisfied regarding a path line length from a press position to the thickness meter and a time until the change in the setting values ​​is reflected in an actual output. Control device.

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