WO2021140747A1 - ロールプレス装置、及び制御装置 - Google Patents

ロールプレス装置、及び制御装置 Download PDF

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Publication number
WO2021140747A1
WO2021140747A1 PCT/JP2020/042737 JP2020042737W WO2021140747A1 WO 2021140747 A1 WO2021140747 A1 WO 2021140747A1 JP 2020042737 W JP2020042737 W JP 2020042737W WO 2021140747 A1 WO2021140747 A1 WO 2021140747A1
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WIPO (PCT)
Prior art keywords
bend
press
cylinder
pressure
bearing portion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2020/042737
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English (en)
French (fr)
Japanese (ja)
Inventor
史紘 寺澤
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Panasonic Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Panasonic Intellectual Property Management Co Ltd filed Critical Panasonic Intellectual Property Management Co Ltd
Priority to CN202080092127.4A priority Critical patent/CN114929463B/zh
Priority to US17/791,820 priority patent/US12580172B2/en
Priority to JP2021569743A priority patent/JP7557790B2/ja
Publication of WO2021140747A1 publication Critical patent/WO2021140747A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M4/00—Electrodes
    • H01M4/02—Electrodes composed of, or comprising, active material
    • H01M4/04—Processes of manufacture in general
    • H01M4/043—Processes of manufacture in general involving compressing or compaction
    • H01M4/0435—Rolling or calendering
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B3/00—Presses characterised by the use of rotary pressing members, e.g. rollers, rings, discs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/28—Control of flatness or profile during rolling of strip, sheets or plates
    • B21B37/38—Control of flatness or profile during rolling of strip, sheets or plates using roll bending
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/10—Energy storage using batteries

Definitions

  • the present disclosure relates to a roll press device for rolling an electrode plate of a secondary battery and a control device.
  • a general secondary battery has a positive electrode, a negative electrode, a separator, and an electrolytic solution as main components.
  • a roll press device is used in the compression processing step, which is one of the steps of manufacturing the positive electrode plate and the negative electrode plate of the secondary battery (see, for example, Patent Document 1).
  • a thickness accuracy of about 2 ⁇ m or less is generally required. Due to the change in the coating thickness of the electrode material in the previous process, or the change in the outer diameter of the roll due to the processing heat due to compression in the compression process and the heat generated by the bearing, the thickness changes in the length direction and width direction of the electrode plate during compression processing. ..
  • the moving time of the active material inside the electrode plate decreases or increases as the transport line accelerates or decelerates, and the filling property of the active material decreases or increases. An increase or decrease in thickness was observed.
  • a method is conceivable in which the thickness of the electrode plate during line transportation is measured with an automatic thickness measuring device, and the thickness is controlled to maintain the target value by feedback control.
  • the feedback control is not in time, and the thickness of the electrode plate changes when the transport line is accelerated or decelerated.
  • the first pressurizing roller and the second pressurizing roller that roll by sandwiching the electrode plate of the secondary battery that is continuously conveyed, and the rotation of the first pressurizing roller.
  • a first main bearing portion and a second main bearing portion that are provided on one side and the other side of the shaft and rotatably support the rotating shaft, and one side of the rotating shaft of the second pressurizing roller.
  • the third main bearing portion and the fourth main bearing portion which are provided on the other side and support the rotating shaft rotatably, and are provided on one side and the other side of the rotating shaft of the first pressurizing roller, respectively.
  • the first bend bearing portion and the second bend bearing portion that rotatably support the rotating shaft, and the rotating shaft are provided on one side and the other side of the rotating shaft of the second pressurizing roller, respectively.
  • the first pressure roller and the second pressure roller are rotatably supported on at least one of the third bend bearing portion and the fourth bend bearing portion, the first main bearing portion, and the third main bearing portion.
  • the first pressurizing roller and the second pressurizing roller are attached to at least one of the first compression mechanism capable of applying a load in a proximity direction and the second main bearing portion and the fourth main bearing portion.
  • the first pressurizing roller and the second pressurizing roller are attached to at least one of the first bend bearing portion and the third bend bearing portion of the second compression mechanism capable of applying a load in a proximity direction.
  • the first pressurizing roller and the second pressurizing roller are attached to at least one of the first bend mechanism capable of applying a load in the direction of disengagement and the second bend bearing portion and the fourth bend bearing portion.
  • a control unit that controls the loads of the first compression mechanism, the second compression mechanism, the first bend mechanism, and the second bend mechanism based on the calculation unit and the set value calculated by the calculation unit.
  • the calculation unit changes in advance the set values of the first compression mechanism and the second compression mechanism so that the change in the thickness of the electrode plate according to the change in the speed of the transfer line of the electrode plate becomes small.
  • FIG. 1 is a schematic front view of the roll press device according to the first embodiment.
  • FIG. 2 is a schematic front view of the roll press device according to the second embodiment.
  • FIG. 3 is a schematic front view of the roll press device according to the third embodiment.
  • FIG. 4 is a schematic side view of the roll press apparatus according to the first to third embodiments.
  • FIG. 5 is a diagram for explaining a feedback control example 1 using the first control panel and the second control panel.
  • FIG. 6 is a diagram for explaining a feedback control example 2 using the first control panel and the second control panel.
  • FIG. 7 is a diagram for explaining a feedback control example 3 using the first control panel and the second control panel.
  • FIG. 8 is a diagram for explaining a feedback control example 4 using the first control panel and the second control panel.
  • FIG. 5 is a diagram for explaining a feedback control example 1 using the first control panel and the second control panel.
  • FIG. 6 is a diagram for explaining a feedback control example 2 using the first control panel and the second
  • FIG. 9 is a diagram plotting the relationship between the change in the thickness of the electrode plate and the change in the line speed under a certain press-bend condition of a certain roll press device.
  • FIG. 10 is a diagram for explaining a feedforward control example 1 using the first control panel.
  • FIG. 11 is a diagram for explaining a feedforward control example 2 using the first control panel.
  • FIG. 12 is a diagram for explaining a feedforward control example 3 using the first control panel.
  • FIG. 1 is a schematic front view of the roll press device according to the first embodiment.
  • the first pressurizing roller 11 and the second pressurizing roller 12 are a pair of upper and lower roll bites, and are installed so as to face each other in a detachable manner.
  • the pair of first pressurizing rollers 11 and second pressurizing rollers 12 roll the electrode plates 2 by sandwiching the electrode plates 2 of the secondary batteries that are continuously conveyed.
  • the electrode plate 2 of the secondary battery passed through the roll press device is a sheet-shaped electrode material obtained by coating a metal foil with a slurry containing an active material and drying it.
  • a positive electrode plate of a lithium ion secondary battery is produced by applying a slurry containing a positive electrode active material such as lithium cobalt oxide or lithium iron phosphate on an aluminum foil.
  • the negative electrode plate of the lithium ion secondary battery is manufactured by applying a slurry containing a negative electrode active material such as graphite on a copper foil. Most of the thickness of the electrode plate 2 passed through the roll press device is the thickness of the applied active material.
  • the first main bearing portion 21 and the second main bearing portion 22 are provided on one side and the other side of the rotating shaft of the first pressure roller 11, respectively, and rotatably support the rotating shaft.
  • the third main bearing portion 23 and the fourth main bearing portion 24 are provided on one side and the other side of the rotating shaft of the second pressure roller 12, respectively, and rotatably support the rotating shaft.
  • the first bend bearing portion 31 and the second bend bearing portion 32 are provided on one side and the other side of the rotating shaft of the first pressure roller 11, respectively, 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 of the rotating shaft of the second pressure roller 12, respectively, and rotatably support the rotating shaft.
  • 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 each have a built-in bearing that rotatably supports the rotating shaft of the roller. It is composed of bearing boxes.
  • the first compression mechanism 41 applies a load to at least one of the first main bearing portion 21 and the third main bearing portion 23 in the direction in which the first pressure roller 11 and the second pressure roller 12 are close to each other. It is a mechanism capable of compressing the electrode plate 2.
  • the second compression mechanism 42 applies a load to at least one of the second main bearing portion 22 and the fourth main bearing portion 24 in the direction in which the first pressure roller 11 and the second pressure roller 12 are close to each other. It is a mechanism capable of compressing the electrode plate 2.
  • the first compression mechanism 41 the first press cylinder 41a capable of applying a load to the third main bearing portion 23 and the first electric screw capable of applying a load to the first main bearing portion 21. 41b is provided.
  • a second press cylinder 42a capable of applying a load to the fourth main bearing portion 24 and a second electric screw 42b capable of applying a load to the second main bearing portion 22 are provided. ..
  • a hydraulic servo valve and a pressure reducing valve can be used for pressure control of the first press cylinder 41a and the second press cylinder 42a.
  • a servomotor is used to control the positions of the first electric screw 41b and the second electric screw 42b.
  • the reduction amounts of the first electric screw 41b and the second electric screw 42b are controlled by their respective servomotors, and the first electric screw 41b and the second electric screw 42b are the first main bearing portion 21 and the second main bearing portion 22.
  • the load applied to each is controlled.
  • the first bend mechanism 51 (in the first embodiment, the first bend cylinder 51a) is provided between the first bend bearing portion 31 and the third bend bearing portion 33, and is provided between the first pressurizing roller 11 and the second pressurization. It is a mechanism that can correct the bending of the rollers by applying a load in the direction in which the rollers 12 come into contact with each other.
  • the second bend mechanism 52 (in the first embodiment, the second bend cylinder 52a) is provided between the second bend bearing portion 32 and the fourth bend bearing portion 34, and is provided between the first pressurizing roller 11 and the second pressurizing portion. It is a mechanism that can correct the bending of the rollers by applying a load in the direction in which the rollers 12 come into contact with each other.
  • the roll gap between the first pressure roller 11 and the second pressure roller 12 is increased. Be controlled.
  • the roll deflection also changes as the roll gap changes.
  • the roll deflection amount can be corrected by changing the pressure of the first bend mechanism 51 and / or the second bend mechanism 52 by the bend pressure control unit 818a (see FIG. 5) described later. At that time, the roll gap also changes, which has the opposite effect of the pressure change caused by the first compression mechanism 41 and / or the second compression mechanism 42.
  • the first preload mechanism 61 (in the example shown in FIG. 1, the first preload cylinder 61a) has a constant load on the first bend bearing portion 31 in the direction in which the first pressure roller 11 and the second pressure roller 12 are separated from each other. It is a mechanism that adds.
  • the second preload mechanism 62 (in the example shown in FIG. 1, the second preload cylinder 62a) has a constant load on the second bend bearing portion 32 in the direction in which the first pressure roller 11 and the second pressure roller 12 are separated from each other. It is a mechanism that adds.
  • the pressures of the first preload cylinder 61a and the second preload cylinder 62a are fixed and are always set to the same pressure.
  • the first preload mechanism 61 and the second preload mechanism 62 apply a preload load equal to or greater than the own weight of the first pressure roller 11 to the first bend bearing portion 31 and the second bend bearing portion 32.
  • the first pressure roller 11 is appropriately pressed (pulled) upward to reduce the influence of rattling of the roll press device.
  • the first preload mechanism 61 and the second preload mechanism 62 can be omitted.
  • FIG. 2 is a schematic front view of the roll press device according to the second embodiment.
  • the first bend cylinder 51a and the first bend cylinder 51a are located 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.
  • a second bend cylinder 52a is provided, and a first bend mechanism 51 and a second bend mechanism 52 of a type in which a load is applied in a direction in which the first pressure roller 11 and the second pressure roller 12 are separated from each other are adopted.
  • a third bend cylinder 51b is provided outside the first bend bearing portion 31, and a fourth bend cylinder 52b is provided outside the second bend bearing portion 32.
  • a fifth bend cylinder 51c is provided outside the third bend bearing portion 33, and a sixth bend cylinder 52c is provided outside the fourth bend bearing portion 34.
  • the type that applies a load to the cylinder is adopted.
  • the first preload mechanism 61 and the second preload mechanism 62 are not provided.
  • the first compression mechanism 41 includes a first press cylinder 41a, a first magnet scale 41c, and a first load cell 41d.
  • a hydraulic servo valve is used for pressure control of the first press cylinder 41a.
  • the first magnet scale 41c detects the position of the first press cylinder 41a.
  • 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. Since the configuration of the second compression mechanism 42 is the same as that of the first compression mechanism 41, the description thereof will be omitted.
  • the first electric screw 41b and the second electric screw 42b are not provided.
  • FIG. 3 is a schematic front view of the roll press device according to the third embodiment.
  • the first bend mechanism 51 and the second bend mechanism 52 of the third embodiment adopt the same type as the first bend mechanism 51 and the second bend mechanism 52 of the second embodiment.
  • the first electric cotter 41e and the second electric cotter 42e are used 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.
  • the roll press apparatus according to the third embodiment can be manufactured at a lower cost than the roll press apparatus according to the first and second embodiments.
  • the first electric cotter 41e is provided between the first main bearing portion 21 and the third main bearing portion 23.
  • the first electric cotter 41e includes an upper cotter fixed to the first main bearing portion 21 and a lower cotter fixed to the third main bearing portion 23.
  • the lower surface of the upper cotter and the upper surface of the lower cotter are tapered surfaces, and are arranged so that the tapered surfaces face each other.
  • the lower cotter is provided with a linear servomotor 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 to the left and right. In the example shown in FIG.
  • 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. Since the configuration of the second electric cotter 42e is the same as that of the first electric cotter 41e, the description thereof will be omitted.
  • FIG. 4 is a schematic side view of the roll press device 1 according to the first to third embodiments.
  • a winding machine 13 is installed on the inlet side of the pair of the first pressure roller 11 and the second pressure roller 12, and a winder 14 is installed on the outlet side.
  • the unwinding machine 13 unwinds the sheet-shaped electrode plate 2 wound in a coil shape toward the pair of the first pressure roller 11 and the second pressure roller 12.
  • the winder 14 winds the electrode plate 2 compressed by the pair of the first pressure roller 11 and the second pressure roller 12 into a coil shape.
  • the motor 15 is a motor that drives the first pressurizing roller 11 and the second pressurizing roller 12.
  • the pulse generator 16 is attached to the driving motor 15 and detects the rotation speed of the motor 15.
  • the thickness gauge 70 is provided on the outlet side of the pair of the first pressure roller 11 and the second pressure roller 12, and the thickness of the electrode plate 2 is set at the first point and the second point where the thickness of the electrode plate 2 is arranged in the width direction of the electrode plate 2. , Detect at 3 points of the 3rd point respectively.
  • 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.
  • the first compression mechanism 41 side in the first to third embodiments the side on which the motor 15 is installed (the first compression mechanism 41 side in the first to third embodiments) and the opposite side (the second compression mechanism 42 side in the first to third embodiments) A screen operated by the operator is installed in. Therefore, in the first to third embodiments, the first point will be referred to as the driving side, the second point will be referred to as the central portion, and the third point will be referred to as the operating side. That is, the thickness gauge 70 detects the thicknesses of the drive side, the central portion, and the operation side of the electrode plate 2 after compression processing, respectively.
  • the thickness gauge 70 scans one thickness detection sensor in the width direction of the electrode plate 2 and continuously detects the thickness of the electrode plate 2, thereby extracting the thicknesses of the drive side, the central portion, and the operation side, respectively. It may be a thing.
  • the thickness gauge 70 is installed with three thickness detection sensors fixed to the drive side, the central portion, and the operation side, and the three thickness detection sensors detect the thicknesses of the drive side, the central portion, and the operation side, respectively. Good.
  • a method may be used in which the distances to both sides of the electrode plate 2 are detected by using a laser sensor or an optical sensor, and the thickness is detected from their positional relationship. Further, the magnetic sensor detects the change in the eddy current to detect the distance to the outer diameter surface of the electrode plate 2, and the laser sensor or the optical sensor detects the distance to the surface of the electrode plate 2 on the guide roll to guide the guide. A method of detecting the thickness from the positional relationship between the roll and the surface of the electrode plate 2 may be used. The distance to the surface of the electrode plate 2 may be detected by using a white confocal sensor.
  • the control device 80 is a device for controlling the entire roll press device 1, and includes a first control panel 81 and a second control panel 82 in the example shown in FIG.
  • the first control panel 81 is a press-based control panel
  • the second control panel 82 is a thickness-based control panel.
  • the rotation pulse generated by the pulse generator 16 is input to the first control panel 81.
  • the thickness detection value detected by the thickness gauge 70 is input to the second control panel 82.
  • the configuration described with reference to FIG. 4 is common to the first to third embodiments.
  • FIG. 5 is a diagram for explaining a feedback control example 1 using the first control panel 81 and the second control panel 82.
  • Feedback control example 1 is a control used in the roll press apparatus according to the first embodiment shown in FIG.
  • the first press cylinder 41a and the second press cylinder 42a are used as the compression mechanism.
  • the first bend cylinder 51a and the second bend cylinder 52a are used as the bend mechanism.
  • the first control panel 81 includes a PLC (Programmable Logic Controller), a PC (Personal Computer), an HMI (Human Machine Interface), an actuator controller, and the like.
  • the second control panel includes a PLC, a PC, a sensor controller, and the like.
  • the program running in the PLC is generated by a dedicated application in the PC and downloaded to the PLC. Further, the product information of the electrode plate 2 is input to the PLC from the MES (Manufacturing Execution System). Further, various setting values input to the operator via the HMI are input to the PLC.
  • the set values include the thickness target 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. included.
  • the HMI accepts operator input, displays driving status, alarms, etc., and outputs voice.
  • FIG. 5 depicts a functional block realized by the first control panel 81 and the second control panel 82, which is related to the 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, and a press pressure control unit 817a. It includes 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.
  • a rotation pulse is input from the pulse generator 16 to the length measuring unit 811.
  • the length measuring unit 811 estimates the rotation speeds of the first pressure roller 11 and the second pressure roller 12 based on the input rotation pulse, and the first pressure roller 11 and the second pressure roller 12 The speed of the electrode plate 2 passing between them is estimated.
  • the length measuring unit 811 measures the length (distance) of the electrode plate 2 per unit time based on the estimated velocity of the electrode plate 2.
  • the length measuring unit 811 supplies the measured length of the electrode plate 2 to the acquisition timing generation unit 812 and the thickness measurement value calculation unit 821.
  • the thickness measurement value calculation unit 821 is input with the thickness detection values of the drive side, the center portion, and the operation side from the thickness gauge 70. Further, the length of the electrode plate 2 is input from the length measuring unit 811.
  • the thickness measurement value calculation unit 821 sets the three thickness detection values as electrodes in order to eliminate high-period thickness fluctuations that do not need to be controlled. Filtering is performed by averaging in the length direction (traveling direction) of the plate 2. In order to eliminate abrupt changes in the traveling direction due to pulsation of the coating pump in the coating process, it is desirable to calculate an average value of 5 mm or more in the traveling direction.
  • the thickness measurement value calculation unit 821 calculates a moving average value of 5 points in the traveling direction and uses it as the measurement value. Further, the average value of 3 points excluding the 2 points that are the most out of the 5 points detected in the traveling direction may be calculated and used as the measured value.
  • the thickness measurement value calculation unit 821 uses the length of the electrode plate 2 input from the length measurement unit 811 as a synchronization signal. The uncoated portion corresponding to the slit in the width direction of the electrode plate 2 and the detected value corresponding to the portion coated on only one side are removed.
  • the thickness measurement value calculation unit 821 has preset widths of the drive side, the center portion, and the operation side, respectively.
  • the average value of the detected values in the range may be calculated and used as the measured value. Further, the measured values may be averaged in the traveling direction as described above to obtain the final measured values.
  • the thickness measurement value calculation unit 821 supplies the calculated drive side thickness measurement value T m , the center thickness measurement value T c , and the operation side thickness measurement value T s to the thickness measurement value acquisition unit 813.
  • the acquisition timing generation unit 812 is the timing at which the thickness measurement value acquisition unit 813 acquires the drive side thickness measurement value T m , the center thickness measurement value T c , and the operation side thickness measurement value T s supplied from the thickness measurement value calculation unit 821. Is generated, and the generated timing is supplied to the thickness measurement value acquisition unit 813.
  • the press cylinders controlled by the hydraulic servo valve the press cylinders controlled by the pressure reducing valve, the electric screw, and the electric cotter, the most responsive is the press cylinder controlled by the hydraulic servo valve.
  • the control system time lag t d is the smallest.
  • the path line length L t and the control system time lag t d are actually measured in advance, and the measured values are set as fixed values in the acquisition timing generation unit 812.
  • the acquisition timing generation unit 812 uses a length parameter L to be compared with the path line length L t and a time parameter t to be compared with 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 sets the control system time lag t d based on the clock supplied from the clock. Increment.
  • the acquisition timing generation unit 812 changes at least one pressure set value of the first press cylinder 41a, the second press cylinder 42a, the first bend cylinder 51a, and the second bend cylinder 52a by the set value correction unit 816, Reset the length parameter L and the time parameter t to zero.
  • the acquisition timing generation unit 812 supplies the acquisition timing to the thickness measurement value acquisition unit 813.
  • the first press cylinder 41a, the second press cylinder 42a, the first bend cylinder 51a, and the second The change in the thickness of the electrode plate 2 due to the change in at least one pressure set value of the bend cylinder 52a is reflected in the detected value of the thickness gauge 70.
  • the first press cylinder 41a, the second press cylinder 42a, and the first bend The change in the thickness of the electrode plate 2 due to the change in at least one pressure set value of the cylinder 51a and the second bend cylinder 52a is not yet reflected in the detected value of the thickness gauge 70. In this state, the influence of the change in the pressure set value on the thickness of the electrode plate 2 has not been confirmed.
  • the thickness measurement value acquisition unit 813 supplies the drive side thickness measurement value T m , the center thickness measurement value T c , and the operation side thickness measurement value T s supplied from the thickness measurement value calculation unit 821 from the acquisition timing generation unit 812. It is acquired at the timing of the measurement and supplied to the feature amount calculation unit 814.
  • the drive-side thickness measurement value T m , the center thickness measurement value T c , and the operation-side thickness measurement value T s are input to the feature amount calculation unit 814 from the thickness measurement value acquisition unit 813. Further, the thickness target value Tt set by the operator is input to the feature amount calculation unit 814.
  • the feature amount calculation unit 814 describes the following thickness feature amount to be controlled based on the drive side thickness measurement value T m , the center thickness measurement value T c , the operation side thickness measurement value T s , and the thickness target value T t.
  • the three deviation feature quantities defined by (Equation 1) to (Equation 3) are calculated.
  • the first feature quantity T t-m is defined by the difference between the thickness target value T t and the driving side thickness measurements T m.
  • the second characteristic quantity T t-s is defined by the difference between the thickness target value T t and the operating side thickness measurements T s.
  • the third feature amount T drop is defined by the difference between the central thickness measurement value T c and the average value of the drive side thickness measurement value T m and the operation side thickness measurement value T s.
  • T t-m T t- T m ... (Equation 1)
  • T t-s T t- T s ... (expression 2)
  • T drop T c- T ms
  • ave T c- (T m + T s ) / 2 ...
  • T s the target thickness T t .
  • the third feature amount T drop represents a secondary component of the thickness profile (when the numerical value is large, an upwardly convex parabolic shape), and changes depending on the magnitude of the roll deflection and the direction of the roll deflection.
  • the feature amount calculation unit 814 supplies the calculated first feature amount T tm , the second feature amount T ts , and the third feature amount T drop to the correction value calculation unit 815.
  • the total press load is the sum of the drive side press load and the operation side press load
  • the total bend load is the sum of the drive side bend load and the operation side bend load
  • the total preload load is the sum of the drive side preload load and the operation side. It is the sum of the preload loads.
  • the drive-side load is a drive-side load generated by the drive-side press cylinder, the drive-side bend cylinder, and the drive-side preload cylinder.
  • the operation side load is an operation side load generated by the operation side press cylinder, the operation side bend cylinder, and the operation side preload cylinder.
  • the press cylinder load works in the direction of applying pressure to the material to be rolled, and the bend load and preload load work in the direction of lowering the pressure on the material to be rolled.
  • the preload cylinder load is set to a fixed value at a pressure that does not cause excessive roll deflection and a pressing pressure that can reduce the rattling and vibration of the equipment. That is, the preload load is not changed in the 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 the bend pressure. In the case of equipment in which the first preload cylinder 61a and the second preload cylinder 62a are not provided, the preload load is zero.
  • A, B, and C in the above (Equation 6) are positive constants, and the difference between the drive side load and the operation side load of the total press load, total bend load, and total preload load is the third feature amount T. It shows that the influence on the drop is different.
  • each load is controlled by controlling the pressure of each cylinder.
  • the driving-side bend pressure B m and the operating side bend pressure B s of the driving-side bend pressure correction value .DELTA.B m and the operating side bend pressure correction value ⁇ B s can be obtained.
  • the pressure of the first press cylinder 41a is set to the corrected drive side press pressure set value P m + ⁇ P m
  • the pressure of the second press cylinder 42a is set to the corrected operation side press pressure set value P s + ⁇ P s.
  • the pressure of 51a becomes the corrected drive side bend pressure set value B m + ⁇ B m
  • the pressure of the second bend cylinder 52a becomes the corrected operation side bend pressure set value B s + ⁇ B s.
  • the correction value calculation unit 815 is supplied with the first feature amount T tm , the second feature amount T ts , and the third feature amount T drop from the feature amount calculation unit 814. Further, the drive side press pressure set value P m , the operation side press pressure set value P s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s input by the operator via the HMI are supplied. To. The drive side press pressure set value P m , the operation side press pressure set value P s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s are the first feature amounts T t under standard conditions. -m, second feature quantity T t-s, is pre-derived value as the third feature amount T drop is all zeros are set, respectively.
  • Correction value calculating unit 815 first feature amount T t-m, the second feature quantity T t-s, the third feature amount T drop, and the equation (7), (8), (Equation 10), ( Based on the proportionality constants of Equations 11), (Equation 13), and (Equation 14), the drive side press pressure correction value ⁇ P m , the operation side press pressure correction value ⁇ P s , the drive side bend pressure correction value ⁇ B m , and the operation.
  • the side bend pressure correction value ⁇ B s is calculated.
  • the correction value calculation unit 815 sets the calculated drive side press pressure correction value ⁇ P m , the operation side press pressure correction value ⁇ P s , the drive side bend pressure correction value ⁇ B m , and the operation side bend pressure correction value ⁇ B s. Supply to 816.
  • the set value correction unit 816 has a drive side press pressure correction value ⁇ P m , an operation side press pressure correction value ⁇ P s , a drive side bend pressure correction value ⁇ B m , and an operation side bend pressure correction value ⁇ B s. Is supplied. Further, the drive side press pressure set value P m , the operation side press pressure set value P s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s input by the operator via the HMI are supplied. To.
  • the set value correction unit 816 corrects the drive side press pressure to the drive side press pressure set value P m , the operation side press pressure set value P s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s.
  • the value ⁇ P m , the operation side press pressure correction value ⁇ P s , the drive side bend pressure correction value ⁇ B m , and the operation side bend pressure correction value ⁇ B s are added, respectively, and the corrected drive side press pressure set value P m + ⁇ P m.
  • the corrected operation side press pressure set value P s + ⁇ P s , the corrected drive side bend pressure set value B m + ⁇ B m , and the corrected operation side bend pressure set value B s + ⁇ B s are calculated.
  • the set value correction unit 816 supplies the calculated corrected drive side press pressure set value P m + ⁇ P m and the corrected operation side press pressure set value P s + ⁇ P s to the press pressure deviation calculation unit 817 c, and after the correction,
  • the drive side bend pressure set value B m + ⁇ B m and the corrected operation side bend pressure set value B s + ⁇ B s are supplied to the bend pressure deviation calculation unit 818c.
  • the press pressure deviation calculation unit 817c is a deviation between the corrected drive side press pressure set value P m + ⁇ P m supplied from the set value correction unit 816 and the measured pressure value of the first press cylinder 41a, and the corrected operation side.
  • the deviation between the press pressure set value P s + ⁇ P s and the measured pressure value of the second press cylinder 42a is calculated, respectively.
  • the measured pressure value of the first press cylinder 41a and the measured pressure value of the second press cylinder 42a can be estimated according to, for example, the measured value of the valve opening meter.
  • 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 operates the pressure of the first press cylinder 41a and 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. Generate a quantity.
  • P compensation may be used instead of PID compensation.
  • the integral term can be controlled
  • I compensation the proportional term (steady state deviation) can be controlled
  • D compensation the differential term can be controlled.
  • the PID control unit 817b supplies the generated pressure operation amount of the first press cylinder 41a and the pressure operation amount of the second press cylinder 42a to the press pressure control unit 817a.
  • the press pressure control unit 817a includes an actuator, and based on the pressure operation amount of the first press cylinder 41a and the pressure operation amount of the second press cylinder 42a, the first press cylinder 41a and the second press cylinder 42a are operated. Drive each.
  • the bend pressure deviation calculation unit 818c is the deviation between the corrected drive side bend pressure set value B m + ⁇ B m supplied from the set value correction unit 816 and the measured pressure value of the first bend cylinder 51a, and the corrected operation side.
  • the deviations between the bend pressure set value B s + ⁇ B s and the measured pressure value of the second bend cylinder 52a are calculated respectively.
  • 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 operates the pressure of the first bend cylinder 51a and 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. Generate a quantity.
  • the PID control unit 818b supplies the generated pressure manipulated amount of the first bend cylinder 51a and the pressure manipulated amount of the second bend cylinder 52a to the bend pressure control unit 818a.
  • the bend pressure control unit 818a includes an actuator, and based on the pressure manipulated amount of the first bend cylinder 51a and the pressure manipulated amount of the second bend cylinder 52a, the first bend cylinder 51a and the fourth bend cylinder 52b To drive each.
  • feedback control is performed so that the pressure of the press cylinder maintains the set value.
  • the operation target is the pressure of the press cylinder.
  • feedback control is performed so that the pressure of the bend cylinder maintains the set value.
  • the operation target is the pressure of the bend cylinder.
  • the thickness of the electrode plate 2 is controlled to the target value by adding the correction value calculated from the thickness measurement value to the set value of the press cylinder pressure and the set value of the bend cylinder pressure.
  • FIG. 6 is a diagram for explaining a feedback control example 2 using the first control panel 81 and the second control panel 82.
  • Feedback control example 2 is a control used in the roll press apparatus according to the second embodiment shown in FIG.
  • the first press cylinder 41a and the second press cylinder 42a are used as the compression mechanism.
  • 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 bend mechanism.
  • the differences from the feedback control example 1 shown in FIG. 5 will be described.
  • a cylinder position control unit 817d instead of the press pressure control unit 817a, the PID control unit 817b, and the press pressure deviation calculation unit 817c, a cylinder position control unit 817d, a PID control unit 817e, and a cylinder position deviation calculation unit 817f are provided.
  • the first feature amount T t m the second feature amount T t t s , the third feature amount T drop , the drive side press cylinder position G m , and the operation side press cylinder position G s.
  • the thickness of the electrode plate 2 does not increase or decrease only by changing the position of the press cylinder, but also considers the amount of elastic deformation of the first pressure roller 11 and the second pressure roller 12 due to the change in the reaction force from the electrode plate 2. There is a need to.
  • the first feature amount T tm and the second feature amount are based on the correlation shown in (Equation 16) and (Equation 17) above.
  • the drive-side press cylinder position G m and the drive-side press cylinder position correction value ⁇ G m and the operation-side press cylinder position correction value ⁇ G s of the operation-side press cylinder position G s are obtained.
  • the cylinder position of the first press cylinder 41a is set to the corrected drive side press cylinder position set value G m + ⁇ G m
  • the cylinder position of the second press cylinder 42a is set to the corrected operation side press cylinder position set value G s + ⁇ G s .
  • the pressures of the 3rd bend cylinder 51b and the 5th bend cylinder 51c are adjusted to the drive side bend pressure set value B m + ⁇ B m
  • the pressures of the 4th bend cylinder 52b and the 6th bend cylinder 52c are corrected to the operation side bend.
  • the cylinder positions of the first press cylinder 41a and the second press cylinder 42a, the third bend cylinder 51b, the fifth bend cylinder 51c, the fourth bend cylinder 52b, and the sixth bend so as to be the pressure set values B s + ⁇ B s, respectively.
  • the pressure of the cylinder 52c By controlling the pressure of the cylinder 52c, the thickness of the electrode plate 2 over the entire width can be controlled to the target value Tt.
  • the correction value calculation unit 815 is supplied with the first feature amount T tm , the second feature amount T ts , and the third feature amount T drop from the feature amount calculation unit 814. Further, the drive side press cylinder position set value G m , the operation side press cylinder position set value G s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s input by the operator via the HMI are Be supplied. The drive side press cylinder position set value G m , the operation side press cylinder position set value G s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s are the first feature quantities under standard conditions. T t-m, the second feature quantity T t-s, is pre-derived value as the third feature amount T drop is all zeros are set, respectively.
  • Correction value calculating unit 815 first feature amount T t-m, the second feature quantity T t-s, the third feature amount T drop, and the (Formula 16), (Equation 17), (Equation 18), ( Based on the proportionality constant of Equation 14), the drive side press cylinder position correction value ⁇ G m , the operation side press cylinder position correction value ⁇ G s , the drive side bend pressure correction value ⁇ B m , and the operation side bend pressure correction value ⁇ B s are set. calculate.
  • the correction value calculation unit 815 sets the calculated drive side press cylinder position correction value ⁇ G m , the operation side press cylinder position correction value ⁇ G s , the drive side bend pressure correction value ⁇ B m , and the operation side bend pressure correction value ⁇ B s. It is supplied to the correction unit 816.
  • the set value correction unit 816 received the drive side press cylinder position correction value ⁇ G m , the operation side press cylinder position correction value ⁇ G s , the drive side bend pressure correction value ⁇ B m , and the operation side bend pressure correction value from the correction value calculation unit 815. ⁇ B s is supplied. Further, the drive side press cylinder position set value G m , the operation side press cylinder position set value G s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s input by the operator via the HMI are Be supplied.
  • the set value correction unit 816 sets the drive side press cylinder position set value G m , the operation side press cylinder position set value G s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s to the drive side press. Cylinder position correction value ⁇ G m , operation side press cylinder position correction value ⁇ G s , drive side bend pressure correction value ⁇ B m , and operation side bend pressure correction value ⁇ B s are added to set the drive side press cylinder position after correction.
  • the set value correction unit 816 supplies the calculated corrected drive side press cylinder position set value G m + ⁇ G m and the corrected operation side press cylinder position set value G s + ⁇ G s to the cylinder position deviation calculation unit 817 f for correction.
  • the subsequent drive side bend pressure set value B m + ⁇ B m and the corrected operation side bend pressure set value B s + ⁇ B s are supplied to the bend pressure deviation calculation unit 818c.
  • the cylinder position deviation calculation unit 817f has the corrected drive side press cylinder position set value G m + ⁇ G m supplied from the set value correction unit 816 and the cylinder position of the first press cylinder 41a measured by the first magnet scale 41c. Calculate the deviation from the measured value of. Further, the cylinder position deviation calculation unit 817f has the corrected operation side press cylinder position set value G s + ⁇ G s supplied from the set value correction unit 816 and the cylinder of the second press cylinder 42a measured by the second magnet scale 42c. Calculate the deviation from the measured value of the position.
  • 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 the PID control unit 817e. Based on the cylinder position deviation of the first press cylinder 41a and the cylinder position deviation of the second press cylinder 42a, the PID control unit 817e operates the pressure of the first press cylinder 41a and the pressure of the second press cylinder 42a. Generate the operation amount of.
  • the PID control unit 817e supplies the generated pressure operation amount of the first press cylinder 41a and the pressure operation amount of the second press cylinder 42a to the cylinder position control unit 817d.
  • the cylinder position control unit 817d includes an actuator, and based on the pressure operation amount of the first press cylinder 41a and the pressure operation amount of the second press cylinder 42a, the first press cylinder 41a and the second press cylinder 42a are operated. Drive each.
  • 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 bend mechanism, but the first bend cylinder 51a in the feedback control example 1 is controlled. Since it is basically the same as the case of controlling the second bend cylinder 52a, the description thereof will be omitted.
  • the feedback control is performed so that the position of the press cylinder maintains the set value, instead of the feedback control so that the pressure of the press cylinder maintains the set value as in the feedback control example 1. ..
  • the operation target is the pressure of the press cylinder.
  • feedback control is performed so that the pressure of the bend cylinder maintains the set value.
  • the operation target is the pressure of the bend cylinder.
  • the thickness of the electrode plate 2 is controlled to the target value by adding the correction value calculated from the thickness measurement value to the set value of the press cylinder position and the set value of the bend cylinder pressure.
  • FIG. 7 is a diagram for explaining a 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 device according to the first embodiment shown in FIG.
  • the first electric screw 41b and the second electric screw 42b are used as the compression mechanism.
  • the first press cylinder 41a and the second press cylinder 42a are subjected to a sufficiently large pressure (fixed value) so that the positions of the cylinders do not change due to the position control of the first electric screw 41b and the second electric screw 42b. Add it.
  • the first bend cylinder 51a and the second bend cylinder 52a are used as the bend mechanism.
  • the differences from the feedback control example 1 shown in FIG. 5 will be described.
  • a screw position control unit 817g, a PID control unit 817h, and a screw position deviation calculation unit 817i are provided.
  • the first feature amount T t m the second feature amount T t t s , the third feature amount T drop , the drive side electric screw position D m , and the operation side electric screw position D s.
  • the thickness of the electrode plate 2 does not increase or decrease only by changing the position of the electric screw, but also considers the amount of elastic deformation of the first pressure roller 11 and the second pressure roller 12 due to the change in the reaction force from the electrode plate 2. There is a need to.
  • Driving side electric screw position D m the operating-side electric screw position D s, an average electric screw position D ave, first feature amount T t-m which represents the thickness of the electrode plate 2, the second feature quantity T t-s, the The correlation with the three feature quantities T drop is experimentally obtained in advance.
  • the position of the first electric cylinder 41b is set to the corrected drive side electric screw position set value D m + ⁇ D m
  • the position of the second electric screw 42b is set to the corrected operation side electric screw position set value D s + ⁇ D s
  • the pressure of the bend cylinder 51a is set to the corrected drive side bend pressure set value B m + ⁇ B m
  • the pressure of the second bend cylinder 52a is set to the corrected operation side bend pressure set value B s + ⁇ B s .
  • the thickness over the entire width of the electrode plate 2 is controlled to the target value Tt. Can be done.
  • the correction value calculation unit 815 is supplied with the first feature amount T tm , the second feature amount T ts , and the third feature amount T drop from the feature amount calculation unit 814. Further, the drive side electric screw position set value D m , the operation side electric screw position set value D s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s input by the operator via the HMI are Be supplied. The drive side electric screw position set value D m , the operation side electric screw position set value D s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s are the first feature quantities under standard conditions. T t-m, the second feature quantity T t-s, is pre-derived value as the third feature amount T drop is all zeros are set, respectively.
  • Correction value calculating unit 815 first feature amount T t-m, the second feature quantity T t-s, the third feature amount T drop, and the (Formula 19), (Equation 20), (Equation 21), ( Based on the proportionality constant of Equation 14), the drive side electric screw position correction value ⁇ D m , the operation side electric screw position correction value ⁇ D s , the drive side bend pressure correction value ⁇ B m , and the operation side bend pressure correction value ⁇ B s are set. calculate.
  • the correction value calculation unit 815 sets the calculated drive side electric screw position correction value ⁇ D m , the operation side electric screw position correction value ⁇ D s , the drive side bend pressure correction value ⁇ B m , and the operation side bend pressure correction value ⁇ B s. It is supplied to the correction unit 816.
  • the drive side electric screw position correction value ⁇ D m is supplied from the correction value calculation unit 815 to the set value correction unit 816. Further, the drive side electric screw position set value D m , the operation side electric screw position set value D s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s input by the operator via the HMI are Be supplied.
  • the set value correction unit 816 sets the drive side electric screw position set value D m , the operation side electric screw position set value D s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s to the drive side electric screw. Add the screw position correction value ⁇ D m , the operation side electric screw position correction value ⁇ D s , the drive side bend pressure correction value ⁇ B m , and the operation side bend pressure correction value ⁇ B s , respectively, and set the drive side electric screw position after correction.
  • the set value correction unit 816 supplies the calculated corrected drive side electric screw position set value D m + ⁇ D m and the corrected operation side electric screw position set value D s + ⁇ D s to the screw position deviation calculation unit 817i for correction.
  • the subsequent drive side bend pressure set value B m + ⁇ B m and the corrected operation side bend pressure set value B s + ⁇ B s are supplied to the bend pressure deviation calculation unit 818c.
  • the screw position deviation calculation unit 817i calculates the deviation between the corrected drive-side electric screw position set value D m + ⁇ D m supplied from the set value correction unit 816 and the measured value of the position of the first electric screw 41b. Further, the screw position deviation calculation unit 817i calculates the deviation between the corrected operation side electric screw position set value D s + ⁇ D s supplied from the set value correction unit 816 and the measured value of the position of the second electric screw 42b. ..
  • the screw position control unit 817g includes a servomotor for reducing the first electric screw 41b and the second electric screw 42b, respectively.
  • the amount of change in the position of each of the first electric screw 41b and the second electric screw 42b can be calculated from the rotation speed of each servomotor.
  • 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 the PID control unit 817h. Based on the position deviation of the first electric screw 41b and the position deviation of the second electric screw 42b, the PID control unit 817h operates the rotation operation amount of the servomotor for the first electric screw 41b and the second electric screw 42b. Generates the amount of rotation of the servo motor for.
  • the PID control unit 817h supplies the generated operation amount of rotation of the servomotor for the first electric screw 41b and the operation amount of rotation of the servomotor for the second electric screw 42b to the screw position control unit 817g.
  • the screw position control unit 817g is based on the amount of rotation of the servomotor for the first electric screw 41b and the amount of operation of rotation of the servomotor for the second electric screw 42b, and the servo for the first electric screw 41b. It drives the motor and the servomotor for the second electric screw 42b, respectively.
  • the feedback control is performed so that the position of the electric screw maintains the set value, instead of the feedback control so that the pressure of the press cylinder maintains the set value as in the feedback control example 1. ..
  • the operation target is the rotation speed of the servo motor.
  • feedback control is performed so that the pressure of the bend cylinder maintains the set value.
  • the operation target is the pressure of the bend cylinder.
  • the thickness of the electrode plate 2 is controlled to the target value by adding the correction value calculated from the thickness measurement value to the set value of the position of the electric screw and the set value of the bend cylinder pressure.
  • FIG. 8 is a diagram for explaining a feedback control example 4 using the first control panel 81 and the second control panel 82.
  • Feedback control example 4 is a control used in the roll press apparatus according to the third embodiment shown in FIG.
  • the first electric cotter 41e and the second electric cotter 42e are used as the compression mechanism.
  • the pressure (fixed value) of the first press cylinder 41a and the second press cylinder 42a is sufficiently large so that the positions of the cylinders do not change due to the height control of the first electric cotter 41e and the second electric cotter 42e. Is added.
  • 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 bend mechanism.
  • the differences from the feedback control example 1 shown in FIG. 5 will be described.
  • a cotter height control unit 817j, a PID control unit 817k, and a cotter height deviation calculation unit 817l are provided. Be done.
  • the press load becomes constant.
  • the load acting on the electrode plate 2 can be changed by changing the height of the cotter to change the load acting on the cotter. It is difficult to measure the load change 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.
  • T tm and the second feature amount are based on the correlation shown in (Equation 22) and (Equation 23) above.
  • T t-s is each driving side electric cotter height K m and the operating-side electric cotter height K s of the driving electric cotter height correction value [Delta] K m and the operating-side electric cotter height correction value [Delta] K s becomes zero at the same time I want it.
  • the height of the first electric cotter 41e is the corrected drive side electric cotter height set value K m + ⁇ K m
  • the height of the second electric cotter 42e is the corrected operation side electric cotter height set value K s + ⁇ K s.
  • the pressures of the third bend cylinder 51b and the fifth bend cylinder 51c are adjusted to the drive side bend pressure set value B m + ⁇ B m
  • the pressures of the fourth bend cylinder 52b and the sixth bend cylinder 52c are corrected.
  • the heights of the first electric cotter 41e and the second electric cotter 42e, the third bend cylinder 51b, the fifth bend cylinder 51c, the fourth bend cylinder 52b, and the sixth so as to be the side bend pressure set values B s + ⁇ B s, respectively.
  • the pressure of the bend cylinder 52c By controlling the pressure of the bend cylinder 52c, the thickness of the electrode plate 2 over the entire width can be controlled to the target value Tt.
  • the correction value calculation unit 815 is supplied with the first feature amount T tm , the second feature amount T ts , and the third feature amount T drop from the feature amount calculation unit 814. Further, the drive side electric cotter height set value K m , the operation side electric cotter height set value K s , the drive side bend pressure set value B m , and the operation side bend pressure set value B input by the operator via the HMI. s is supplied.
  • the drive side electric cotter height set value K m , the operation side electric cotter height set value K s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s are the first under standard conditions.
  • feature amount T t-m, the second feature quantity T t-s, is pre-derived value as the third feature amount T drop is all zeros are set, respectively.
  • Correction value calculating unit 815 first feature amount T t-m, the second feature quantity T t-s, the third feature amount T drop, and the (Formula 22), (Equation 23), (Equation 24), ( Based on the proportionality constant of Equation 14), the drive side electric cotter height correction value ⁇ K m , the operation side electric cotter height correction value ⁇ K s , the drive side bend pressure correction value ⁇ B m , and the operation side bend pressure correction value ⁇ B. Calculate s.
  • the correction value calculation unit 815 calculates the calculated drive side electric cotter height correction value ⁇ K m , the operation side electric cotter height correction value ⁇ K s , the drive side bend pressure correction value ⁇ B m , and the operation side bend pressure correction value ⁇ B s . It is supplied to the set value correction unit 816.
  • the set value correction unit 816 has a drive side electric cotter height correction value ⁇ K m , an operation side electric cotter height correction value ⁇ K s , a drive side bend pressure correction value ⁇ B m , and an operation side bend pressure.
  • the correction value ⁇ B s is supplied.
  • the drive side electric cotter height set value K m , the operation side electric cotter height set value K s , the drive side bend pressure set value B m , and the operation side bend pressure set value B input by the operator via the HMI. s is supplied.
  • the set value correction unit 816 drives the drive side electric cotter height set value K m , the operation side electric cotter height set value K s , the drive side bend pressure set value B m , and the operation side bend pressure set value B s .
  • the drive side after correction by adding the side electric cotter height correction value ⁇ K m , the operation side electric cotter height correction value ⁇ K s , the drive side bend pressure correction value ⁇ B m , and the operation side bend pressure correction value ⁇ B s, respectively.
  • Electric cotter height setting value K m + ⁇ K m corrected operation side electric cotter height setting value K s + ⁇ K s , corrected drive side bend pressure setting value B m + ⁇ B m , and corrected operation side bend pressure setting Calculate the value B s + ⁇ B s.
  • the set value correction unit 816 supplies the calculated corrected drive side electric cotter height set value K m + ⁇ K m and the corrected operation side electric cotter height set value K s + ⁇ K s to the cotter height deviation calculation unit 817 l. Then, the corrected drive side bend pressure set value B m + ⁇ B m and the corrected operation side bend pressure set value B s + ⁇ B s are supplied to the bend pressure deviation calculation unit 818 c.
  • the cotter height deviation calculation unit 817l determines the deviation between the corrected drive-side electric cotter height set value K m + ⁇ K m supplied from the set value correction unit 816 and the measured value of the height of the first electric cotter 41e. calculate. Further, the cotter height deviation calculation unit 817l is a deviation between the corrected operation side electric cotter height set value K s + ⁇ K s supplied from the set value correction unit 816 and the measured value of the height of the second electric cotter 42e. Is calculated.
  • the cotter height control unit 817j includes a linear servomotor for sliding the lower cotters of the first electric cotter 41e and the second electric cotter 42e in the left-right direction, respectively.
  • the amount of change in 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 servomotor.
  • a range finder is provided between the first main bearing portion 21 and the third main bearing portion 23 to measure the height of the first electric cotter 41e, and a range finder is provided between the second main bearing portion 22 and the fourth main bearing portion 24. It may be provided and the height of the second electric cotter 42e may be measured respectively.
  • 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 the PID control unit 817k. Based on the height deviation of the first electric cotter 41e and the height deviation of the second electric cotter 42e, the PID control unit 817k operates the movement of the linear servomotor for the first electric cotter 41e and the second. The operation amount of the movement of the linear servomotor for the electric cotter 42e is generated.
  • the PID control unit 817k supplies the generated operation amount of the linear servomotor for the first electric cotter 41e and the operation amount of the movement of the linear servomotor for the second electric cotter 42e to the cotter height control unit 817j.
  • the cotter height control unit 817j is based on the movement operation amount of the linear servomotor for the first electric cotter 41e and the movement operation amount of the linear servomotor for the second electric cotter 42e, and the first electric cotter 41e
  • the linear servomotor for the second electric cotter 42e and the linear servomotor for the second electric cotter 42e are driven respectively.
  • 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 bend mechanism, but the first bend cylinder 51a in the feedback control example 1 is controlled. Since it is basically the same as the case of controlling the second bend cylinder 52a, the description thereof will be omitted.
  • the feedback control is performed so that the height of the electric cotter maintains the set value, instead of the feedback control so that the pressure of the press cylinder maintains the set value as in the feedback control example 1.
  • the operation target is the amount of movement of the linear servo motor.
  • feedback control is performed so that the pressure of the bend cylinder maintains the set value.
  • the operation target is the pressure of the bend cylinder.
  • the thickness of the electrode plate 2 is controlled to the target value by adding the correction value calculated from the thickness measurement value to the set value of the height of the electric cotter and the set value of the bend cylinder pressure.
  • first press cylinder 41a When using a hydraulic cylinder, it is desirable to install a hydraulic control device as close as possible to the hydraulic cylinder. Further, it is desirable to use a hydraulic servo valve having a high pressure control speed as the hydraulic control device. As a result, it is possible to prevent a delay in pressure response and pressure hunting due to a pressure change in the hydraulic piping due to a pressure change in the hydraulic cylinder.
  • the transfer line is accelerated or decelerated. It is difficult to correct the thickness change with high accuracy. It is conceivable to slow down the speed of the transport line during acceleration or deceleration, but in that case, the production efficiency is reduced. Therefore, a method of predicting a change in the thickness of the electrode plate 2 due to a change in the speed of the transport line and correcting the thickness of the electrode plate 2 by feedforward control is introduced.
  • FIG. 9 is a diagram plotting the relationship between the change in the thickness of the electrode plate 2 and the change in the line speed under a certain press / bend condition of a certain roll press device 1.
  • the horizontal axis represents the line speed [mpm]
  • the vertical axis represents the average thickness width [ ⁇ m] of the electrode plate 2. As shown in FIG. 9, it can be seen that the thickness of the electrode plate 2 increases as the line speed increases.
  • FIG. 10 is a diagram for explaining a feedforward control example 1 using the first control panel 81.
  • Feedforward control example 1 is a control used in the roll press apparatus according to the first embodiment shown in FIG.
  • the first press cylinder 41a and the second press cylinder 42a are used as the compression mechanism.
  • the bend mechanism is not used for feedforward control in order to simplify the feedforward control.
  • FIG. 10 depicts a functional block 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 set value correction unit 816, a press pressure control unit 817a, a PID control unit 817b, and a press pressure deviation calculation unit 817c. including.
  • the line speed control unit 8110 is based on the command value of the line speed supplied from the line speed setting change unit 819, the rotation speed of the unwinder 13, the rotation of the first pressurizing roller 11 and the rotation of the second pressurizing roller 12. The speed and the rotation speed of the winder 14 are controlled.
  • the line speed set by the operator is input to the line speed setting change unit 819.
  • the acceleration during acceleration of the transport line and the deceleration during deceleration are basically preset by the manufacturer of the roll press device 1. The specifications may be such that the acceleration during acceleration and the deceleration during deceleration can be set and changed by the user.
  • feedforward control example 1 the change in the thickness of the electrode plate 2 due to the change in the line speed is predicted, the press load required to maintain the thickness of the electrode plate 2 is calculated, and the press load is changed by the feedforward control. Let me. By experimentally investigating the relationship between the line speed and the thickness of the electrode plate 2, an appropriate press pressure can be predicted with high accuracy.
  • the line speed V s S seconds after the start of acceleration or deceleration is the speed V 0 at the start of acceleration or deceleration and the speed V 0 at the start of acceleration or deceleration.
  • the amount of change ⁇ V s of the line speed after S seconds it can be defined as follows (Equation 25).
  • the amount of change ⁇ V s of the line speed after S seconds from the start of acceleration or deceleration can be defined as follows (Equation 26).
  • the relationship between the change amount ⁇ V of the line speed and the change amount ⁇ T ave of the thickness average value T ave may be obtained experimentally and fitted by a multidimensional function, an exponential function, or a logarithmic function.
  • linear pressure the average value Lave (hereinafter referred to as linear pressure) of the press load acting on the electrode plate 2 in the width direction and the thickness average value Tave after pressing are in a proportional relationship
  • linear pressure is determined.
  • Equation 28 the linear pressure relationship holds between the amount of change in linear pressure ⁇ L ave and the amount of change in average thickness T ave ⁇ T ave when changed.
  • the linear pressure correction values ⁇ L ave, s for making the change amount ⁇ T ave, s of the thickness average value T ave S seconds after the start of acceleration or deceleration to zero are the above (Equation 26), (Equation 27), (Equation 27).
  • ⁇ V s and ⁇ T ave can be removed from the relationship of Eq. 28) and obtained by the following (Equation 29).
  • the press acting on the electrode plate 2 by keeping the positions of the first electric screw 41b and the second electric screw 42b constant and changing the pressures of the first press cylinder 41a and the second press cylinder 42a. Change the load.
  • the average press pressure P ave (P m + P s ) / 2 change amount ⁇ P ave of the drive side press pressure P m and the operation side press pressure P s , and the change amount ⁇ T ave of the thickness average value T ave of the electrode plate 2 since during a proportional relationship, when varying the pressing pressure, between the variation [Delta] T ave of the average pressing pressure P ave of the variation [Delta] P ave and the thickness average value T ave is represented by the following (equation 30) The relationship holds.
  • the differential pressure between the drive side press pressure P m and the operation side press pressure P s during the acceleration period or deceleration period of the transport line may be basically the same as before acceleration or deceleration. If the change in thickness of the electrode plate 2 due to the change in line speed differs between the drive side and the operation side due to the difference in rigidity between the drive side and the operation side of the roll press device 1, the differential pressure during the acceleration period or the deceleration period is used. It may be changed.
  • the correction value calculation unit 815 is supplied with the acceleration start time, the acceleration end time, the line speed V 0 at the start of acceleration, and the acceleration ⁇ from the line speed setting changing unit 819 before the start of acceleration of the transfer line. For example, when the roll press device 1 is started up and when the line speed is changed during the start-up, the line speed setting changing unit 819 supplies such information. Further, the correction value calculation unit 815 is supplied with the deceleration start time, the deceleration end time, the line speed V 0 at the deceleration start, and the deceleration ⁇ before the deceleration start of the transport line from the line speed setting changing unit 819. ..
  • the correction value calculation unit 815 calculates the amount of change ⁇ V s of the line speed S seconds after the start of acceleration based on the above (Equation 26), the line speed V 0 at the start of acceleration and the acceleration ⁇ .
  • the correction value calculation unit 815 applies the calculated change amount ⁇ V s of the line speed to the above (Equation 27), and predicts the change amount ⁇ T ave, s of the thickness average value T ave S seconds after the start of acceleration.
  • the correction value calculation unit 815 calculates the correction value ⁇ P ave, s of the average press pressure Pave for making the change amount ⁇ T ave, s of the thickness average value T ave zero. ..
  • the correction value calculating unit 815 an average pressing pressure P ave of the correction value [Delta] P 0.1 0.1 second intervals, [Delta] P 0.2, ⁇ ⁇ ⁇ , average pressing pressure P to calculate the [Delta] P t end, was calculated correction value [Delta] P 0.1 of ave, ⁇ P 0.2, ⁇ , supplies [Delta] P t end the set value correcting section 816.
  • the set value correcting section 816 the correction value [Delta] P 0.1 of the average pressing pressure P ave from the correction value calculating unit 815, [Delta] P 0.2, ⁇ ⁇ ⁇ , the [Delta] P t end is supplied.
  • the set value correction unit 816 adds the correction values ⁇ P 0.1 , ⁇ P 0.2 , ..., ⁇ P tend to the press pressure set value P 0 at the start of acceleration, respectively, and the corrected press pressure set value P 0 + ⁇ P 0.1. , P 0 + ⁇ P 02 , ⁇ , P 0 + ⁇ P tend is calculated.
  • the press pressure set value P 0 at the start of acceleration is, for example, a press pressure set value P input by the operator via the HMI.
  • the set value correction unit 816 supplies the calculated corrected press pressure set values P 0 + ⁇ P 0.1 , P 0 + ⁇ P 02 , ..., P 0 + ⁇ P tend to the press pressure deviation calculation unit 817c.
  • the press pressure deviation calculation unit 817c is assigned to the first press cylinder 41a of the corrected press pressure set values P 0 + ⁇ P 0.1 , P 0 + ⁇ P 02 , ..., P 0 + ⁇ P tend supplied from the set value correction unit 816.
  • the deviation between the set value of the press pressure and the measured pressure value of the first press cylinder 41a is calculated at each time.
  • the press pressure deviation calculation unit 817c is attached to the second press cylinder 42a of the corrected press pressure set values P 0 + ⁇ P 0.1 , P 0 + ⁇ P 02 , ..., P 0 + ⁇ P tend supplied from the set value correction unit 816.
  • the deviation between the assigned press pressure set value and the measured pressure value of the second press cylinder 42a is calculated at each time.
  • the measured pressure value of the first press cylinder 41a and the measured pressure value of the second press cylinder 42a can be estimated according to, for example, the measured value of the valve opening meter.
  • 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 operates the pressure of the first press cylinder 41a and 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. Generate a quantity.
  • the PID control unit 817b supplies the generated pressure operation amount of the first press cylinder 41a and the pressure operation amount of the second press cylinder 42a to the press pressure control unit 817a.
  • the press pressure control unit 817a includes an actuator, and based on the pressure operation amount of the first press cylinder 41a and the pressure operation amount of the second press cylinder 42a, the first press cylinder 41a and the second press cylinder 42a are operated. Drive each. In the above explanation, acceleration is assumed, but the same control is applied during deceleration.
  • the line speed setting change unit 819 instructs the line speed control unit 8110 to change the line speed at a timing corresponding to a time lag t e from the timing of instructing the correction value calculation unit 815 to change the set value of the press pressure. Supply the value.
  • the operation of the actuator can be changed more appropriately with respect to the change in the line speed, and the thickness of the electrode plate 2 can be corrected with high accuracy.
  • FIG. 11 is a diagram for explaining a feedforward control example 2 using the first control panel 81.
  • Feedforward control example 2 is a control used in the roll press apparatus according to the second embodiment shown in FIG.
  • the first press cylinder 41a and the second press cylinder 42a are used as the compression mechanism.
  • the differences from the feedforward control example 1 shown in FIG. 10 will be described.
  • feedforward control example 2 instead of the press pressure control unit 817a, the PID control unit 817b, and the press pressure deviation calculation unit 817c, a cylinder position control unit 817d, a PID control unit 817e, and a cylinder position deviation calculation unit 817f are provided. ..
  • the press acting on the electrode plate 2 by keeping the positions of the first electric screw 41b and the second electric screw 42b constant and changing the pressures of the first press cylinder 41a and the second press cylinder 42a. Change the load.
  • the cylinder position of the first press cylinder 41a is measured by the first magnet scale 41c, and the pressure of the first press cylinder 41a is controlled so that the cylinder position of the first press cylinder 41a maintains the set value.
  • the cylinder position of the second press cylinder 42a is measured by the second magnet scale 42c, and the pressure of the second press cylinder 42a is controlled so that the cylinder position of the second press cylinder 42a maintains the set value.
  • the correction value ⁇ G ave, s of the average press cylinder position Gave for making the change amount ⁇ T ave, s of the thickness average value T ave S seconds after the start of acceleration or deceleration to zero is the above (Equation 26), (Equation 26). 27), ⁇ V s and ⁇ Tave are removed from the relationship of (Equation 32), and it can be obtained by the following (Equation 33).
  • the difference between the drive side press cylinder position G m and the operation side press cylinder position G s during the acceleration period or deceleration period of the transport line may be basically the same as before acceleration or deceleration. If the change in thickness of the electrode plate 2 due to the change in line speed differs between the drive side and the operation side due to the difference in rigidity between the drive side and the operation side of the roll press device 1, the difference in the acceleration period or the deceleration period is changed. You may let me.
  • the correction value calculation unit 815 is supplied with the acceleration start time, the acceleration end time, the line speed V 0 at the start of acceleration, and the acceleration ⁇ from the line speed setting changing unit 819 before the start of acceleration of the transfer line. Further, the correction value calculation unit 815 is supplied with the deceleration start time, the deceleration end time, the line speed V 0 at the deceleration start, and the deceleration ⁇ before the deceleration start of the transport line from the line speed setting changing unit 819. ..
  • the correction value calculation unit 815 calculates the amount of change ⁇ V s of the line speed S seconds after the start of acceleration based on the above (Equation 26), the line speed V 0 at the start of acceleration and the acceleration ⁇ .
  • the correction value calculation unit 815 applies the calculated change amount ⁇ V s of the line speed to the above (Equation 27), and predicts the change amount ⁇ T ave, s of the thickness average value T ave S seconds after the start of acceleration.
  • the correction value calculation unit 815 calculates the correction value ⁇ G ave, s of the average press cylinder position Gave for making the change amount ⁇ T ave, s of the thickness average value T ave zero. To do.
  • the correction value calculation unit 815 calculates the correction values ⁇ G 0.1 , ⁇ G 0.2 , ..., ⁇ G tend of the average press cylinder position Gave at intervals of 0.1 seconds, and the calculated average press cylinder.
  • the correction values ⁇ G 0.1 , ⁇ G 0.2 , ..., ⁇ G tend of the position G ave are supplied to the set value correction unit 816.
  • the set value correcting section 816, the correction value .DELTA.G 0.1 average press cylinder position G ave from the correction value calculating unit 815, ⁇ G 0.2, ⁇ , ⁇ G tend is supplied.
  • the set value correction unit 816 adds the correction values ⁇ G 0.1 , ⁇ G 0.2 , ..., ⁇ G tend to the press cylinder position setting value G 0 at the start of acceleration, respectively, and the corrected press cylinder position setting value G 0.
  • the press cylinder position setting value G 0 at the start of acceleration is, for example, a press cylinder position setting value G input by the operator via the HMI.
  • the set value correction unit 816 supplies the calculated corrected press cylinder position set values G 0 + ⁇ G 0.1 , G 0 + ⁇ G 02 , ..., G 0 + ⁇ G tend to the cylinder position deviation calculation unit 817f.
  • the cylinder position deviation calculation unit 817f includes the corrected press cylinder position set values G 0 + ⁇ G 0.1 , G 0 + ⁇ G 02 , ..., G 0 + ⁇ G tend supplied from the set value correction unit 816, and the first magnet scale 41c. The deviation from the measured value of the cylinder position of the first press cylinder 41a measured by the above is calculated at each time. Further, the cylinder position deviation calculation unit 817f has a corrected press cylinder position set value G 0 + ⁇ G 0.1 , G 0 + ⁇ G 02 , ..., G 0 + ⁇ G tend supplied from the set value correction unit 816, and a second magnet scale. The deviation from the measured value of the cylinder position of the second press cylinder 42a measured by 42c is calculated at each time.
  • 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 the PID control unit 817e. Based on the cylinder position deviation of the first press cylinder 41a and the cylinder position deviation of the second press cylinder 42a, the PID control unit 817e operates the pressure of the first press cylinder 41a and the pressure of the second press cylinder 42a. Generate the operation amount of.
  • the PID control unit 817e supplies the generated pressure operation amount of the first press cylinder 41a and the pressure operation amount of the second press cylinder 42a to the cylinder position control unit 817d.
  • the cylinder position control unit 817d includes an actuator, and based on the pressure operation amount of the first press cylinder 41a and the pressure operation amount of the second press cylinder 42a, the first press cylinder 41a and the second press cylinder 42a are operated. Drive each. In the above explanation, acceleration is assumed, but the same control is applied during deceleration.
  • the line speed setting change unit 819 instructs the line speed control unit 8110 to change the line speed at a timing corresponding to a time lag t e from the timing of instructing the correction value calculation unit 815 to change the set value of the cylinder position. Supply the value.
  • the operation of the actuator can be changed more appropriately with respect to the change in the line speed, and the thickness of the electrode plate 2 can be corrected with high accuracy.
  • feedforward control example 2 the change in the thickness of the electrode plate 2 due to the change in the line speed is predicted, the press cylinder position required to keep the thickness of the electrode plate 2 constant is calculated, and the press cylinder position is set. Change by feedforward control. As a result, changes in the thickness of the electrode plate 2 during the acceleration period or deceleration period of the transport line can be suppressed with high accuracy.
  • FIG. 12 is a diagram for explaining a 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 the first embodiment shown in FIG.
  • the first electric screw 41b and the second electric screw 42b are used as the compression mechanism.
  • the differences from the feedforward control example 1 shown in FIG. 10 will be described.
  • feedforward control example 3 instead of the press pressure control unit 817a, the PID control unit 817b, and the press pressure deviation calculation unit 817c, a screw position control unit 817g, a PID control unit 817h, and a screw position deviation calculation unit 817i are provided. ..
  • the pressure (1) and the second press cylinder 42a are sufficiently large so that the cylinder positions do not change due to the position change of the first electric screw 41b and the second electric screw 42b. (Fixed value) is added.
  • the press load acting on the electrode plate 2 is changed.
  • the positions of the first electric screw 41b and the second electric screw 42b are controlled by a servomotor.
  • the difference between the drive side electric screw position D m and the operation side electric screw position D s during the acceleration period or deceleration period of the transport line may be basically the same as before acceleration or deceleration. If the change in thickness of the electrode plate 2 due to the change in line speed differs between the drive side and the operation side due to the difference in rigidity between the drive side and the operation side of the roll press device 1, the difference in the acceleration period or the deceleration period is changed. You may let me.
  • the correction value calculation unit 815 is supplied with the acceleration start time, the acceleration end time, the line speed V 0 at the start of acceleration, and the acceleration ⁇ from the line speed setting changing unit 819 before the start of acceleration of the transfer line. Further, the correction value calculation unit 815 is supplied with the deceleration start time, the deceleration end time, the line speed V 0 at the deceleration start, and the deceleration ⁇ before the deceleration start of the transport line from the line speed setting changing unit 819. ..
  • the correction value calculation unit 815 calculates the amount of change ⁇ V s of the line speed S seconds after the start of acceleration based on the above (Equation 26), the line speed V 0 at the start of acceleration and the acceleration ⁇ .
  • the correction value calculation unit 815 applies the calculated change amount ⁇ V s of the line speed to the above (Equation 27), and predicts the change amount ⁇ T ave, s of the thickness average value T ave S seconds after the start of acceleration.
  • the correction value calculation unit 815 calculates the correction value ⁇ D ave, s of the average electric screw position D ave for making the change amount ⁇ T ave, s of the thickness average value T ave zero. To do.
  • the correction value calculation unit 815 calculates the correction values ⁇ D 0.1 , ⁇ D 0.2 , ..., ⁇ D tend of the average electric screw position Dave at 0.1 second intervals, and the calculated average electric screw.
  • the correction values ⁇ D 0.1 , ⁇ D 0.2 , ..., ⁇ D tend of the position D ave are supplied to the set value correction unit 816.
  • the set value correcting section 816 the correction value [Delta] D 0.1 of the average electric screw position D ave from the correction value calculating unit 815, ⁇ D 0.2, ⁇ , ⁇ D tend is supplied.
  • the set value correction unit 816 adds the correction values ⁇ D 0.1 , ⁇ D 0.2 , ..., ⁇ D tend to the electric screw position set value D 0 at the start of acceleration, respectively, and the corrected electric screw position set value D 0.
  • the electric screw position setting value D 0 at the start of acceleration is, for example, the electric screw position setting value D input by the operator via the HMI.
  • the set value correction unit 816 supplies the calculated corrected electric screw position set values D 0 + ⁇ D 0.1 , D 0 + ⁇ D 02 , ..., D 0 + ⁇ D tend to the screw position deviation calculation unit 817i.
  • the screw position deviation calculation unit 817i includes the corrected electric screw position set values D 0 + ⁇ D 0.1 , D 0 + ⁇ D 02 , ..., D 0 + ⁇ D tend and the first electric screw 41b supplied from the set value correction unit 816. The deviation from the measured value of the position of is calculated at each time. Further, the screw position deviation calculation unit 817i has the corrected electric screw position set values D 0 + ⁇ D 0.1 , D 0 + ⁇ D 02 , ..., D 0 + ⁇ D tend supplied from the set value correction unit 816, and the second electric screw. The deviation from the measured value of the position 42b is calculated at each time.
  • the screw position control unit 817g includes a servomotor for reducing the first electric screw 41b and the second electric screw 42b, respectively.
  • the amount of change in the position of each of the first electric screw 41b and the second electric screw 42b can be calculated from the rotation speed of each servomotor.
  • 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 the PID control unit 817h. Based on the position deviation of the first electric screw 41b and the position deviation of the second electric screw 42b, the PID control unit 817h operates the rotation operation amount of the servomotor for the first electric screw 41b and the second electric screw 42b. Generates the amount of rotation of the servo motor for.
  • the PID control unit 817h supplies the generated operation amount of rotation of the servomotor for the first electric screw 41b and the operation amount of rotation of the servomotor for the second electric screw 42b to the screw position control unit 817g.
  • the screw position control unit 817g is based on the amount of rotation of the servomotor for the first electric screw 41b and the amount of operation of rotation of the servomotor for the second electric screw 42b, and the servo for the first electric screw 41b. It drives the motor and the servomotor for the second electric screw 42b, respectively. In the above explanation, acceleration is assumed, but the same control is applied during deceleration.
  • the line speed setting change unit 819 changes the line speed to the line speed control unit 8110 at a timing corresponding to a time lag t e from the timing of instructing the correction value calculation unit 815 to change the set value of the electric screw position. Supply the command value.
  • the operation of the servomotor can be changed more appropriately with respect to the change in the line speed, and the thickness of the electrode plate 2 can be corrected with high accuracy.
  • feedforward control example 3 the change in the thickness of the electrode plate 2 due to the change in the line speed is predicted, the electric screw position required to keep the thickness of the electrode plate 2 constant is calculated, and the electric screw position is set. Change by feedforward control. As a result, changes in the thickness of the electrode plate 2 during the acceleration period or deceleration period of the transport line can be suppressed with high accuracy.
  • the compression mechanism and / or the bend mechanism is controlled so that m, the second feature T ts , and the third feature T drop are all zero.
  • the compression mechanism a press mechanism or a cotter mechanism can be used. As a result, the thickness of the electrode plate 2 after compression processing can be converged to the target value Tt over the entire width.
  • Patent Document 1 Japanese Unexamined Patent Publication No. 2013-11167
  • the thickness after compression is measured at three locations on the operation side, the central portion, and the drive side, and the difference between the measured thickness value and the target thickness is set in advance.
  • a method of controlling the press mechanism and the bend mechanism so as to enter the threshold value when the threshold value is exceeded is disclosed.
  • the film thickness control since the film thickness control is not activated until the threshold value is exceeded, the thickness accuracy higher than the threshold value cannot be obtained, and it takes time to converge to the vicinity of the target thickness, or the target is set. It may not be possible to converge near the thickness.
  • the drive side thickness, the operation side thickness, and the target thickness are compared, and when at least one of the drive side thickness and the operation side thickness exceeds the threshold value, the position of the press cylinder is repositioned so as to correct this.
  • the pressure of the bend cylinder is calculated and set in order to set and maintain the amount of deflection correction that changes due to the position change of the press cylinder. If both the drive side thickness and the operation side thickness do not exceed the threshold value, the central part thickness and the threshold value are compared, and if the threshold value is exceeded, the roll deformation of the central part is assumed to be large, and the bend cylinder Only the pressure of the press cylinder is changed, and the position of the press cylinder is not changed. These control flows are repeated and executed.
  • the pressure change of the bend cylinder acts in the direction of opening the roll gap and changes the rolling load on the material to be rolled, so that the thickness changes. Therefore, in any of the procedures in the above control flow, the film thickness changes by changing the pressure of the bend cylinder, and the threshold value is exceeded again, and it takes time to reach the target thickness. Or, there are cases where the threshold cannot be controlled. In particular, the narrower the threshold value, or the more the position of the press cylinder or the pressure of the bend cylinder needs to be changed, the more likely it is that the threshold value will be exceeded again. There is a limit to.
  • the thickness on the drive side, the thickness on the operation side, and the target thickness are compared, and if both the thickness on the drive side and the thickness on the operation side do not exceed the threshold value, the thickness at the center and the threshold value are compared. If it exceeds the value, it is judged that the roll deflection is large, and only the pressure of the bend cylinder is changed. In this case, since the thickness at both ends is controlled to be equal to or less than the threshold value and then the center thickness is controlled, it takes time to converge to the target thickness. Further, in the process of controlling the thickness at both ends, the central thickness may deviate from the target thickness.
  • the load on both sides is controlled to be reduced so that the thickness at both ends becomes the target thickness, but it acts on the central portion of the electrode plate. Since the pressure from the press roll is also reduced, the central thickness becomes thicker and the target value is deviated.
  • the magnitude of the roll deflection and the direction of the roll deflection are the difference between the center thickness and the average thickness at both ends (the difference between the center thickness and the average thickness at both ends). Judging by the third feature amount T drop ), while controlling the thickness at both ends, the difference in thickness between the center and both ends due to roll bending is controlled at the same time. As a result, it is possible to quickly converge the thickness of the electrode plate 2 to the target value over the entire width without deteriorating the thickness in the width direction.
  • the thickness of the electrode plate 2 after compression processing is always converged to the target value Tt.
  • the thickness of the electrode plate 2 is always maintained in a good state.
  • the operator since the thickness of the electrode plate 2 is automatically controlled to the target value Tt , the operator periodically stops the line, measures the thickness of the electrode plate 2 with a micrometer, and based on the measured value, the compression mechanism and / Or there is no need to adjust the pressure value of the bend mechanism. Therefore, it is not necessary to assign a skilled operator, and labor costs can be suppressed. In addition, it is possible to suppress variations in quality depending on the operator.
  • the correction of the new set value is executed based on the thickness measurement value before the correction of the set value is reflected.
  • the correction thickness measured value is acquired after the time t d until it is reflected has elapsed.
  • Three feature quantities are calculated based on the acquired thickness measurement values, correction values are calculated based on the three feature quantities, and the next set value change is executed.
  • the feedforward control examples 1 to 3 together, it is possible to suppress the change in the thickness of the electrode plate 2 at the time of acceleration or deceleration of the transport line with high accuracy. That is, by predicting the change in the thickness of the electrode plate 2 due to the change in the line speed, calculating the compression condition for making the predicted thickness change zero, and controlling the compression mechanism in feedforward, the thickness due to the change in the line speed is obtained. Changes can be suppressed with high accuracy.
  • control device 80 is composed of two control panels, a first control panel 81 and a second control panel 82, has been described, but one in which the first control panel 81 and the second control panel 82 are integrated. It may be composed of a control panel.
  • the compression mechanism and / or the bend mechanism are set so that the first feature amount T tm , the second feature amount T ts , and the third feature amount T drop are all zero.
  • An example of controlling is described.
  • the electrode plate 2 is flat in the width direction.
  • a compression mechanism and / or a bend mechanism is provided so that the third feature amount T drop becomes a negative value according to the thickness difference between the edge and the center.
  • the compression mechanism and / or the bend mechanism is controlled so that the third feature amount T drop becomes a positive value according to the thickness difference between the edge and the center.
  • the electrode plate 2 having an arbitrary thickness profile can be manufactured by arbitrarily setting ⁇ , ⁇ , and ⁇ of the following (Equation 35) to (Equation 37).
  • the third feature amount indicating the secondary component of the thickness profile of the electrode plate is the central thickness measurement value T c , the drive side thickness measurement value T m, and the operation side thickness measurement value T s. It is specified by the difference from the average value of.
  • the third feature amount can be defined from a quadratic or quaternary approximate curve derived by using the least squares method based on the thickness measurement values of three or more points.
  • the feature amount calculation unit 814 sets the quadratic coefficient of the approximated quadratic curve to the third feature amount.
  • the feature amount calculation unit 814 sets the quadratic coefficient of the approximated quadratic curve as the third feature amount.
  • the larger the number of sample points the better the approximation accuracy. Further, if it is a function of quadratic or higher, a quadratic coefficient can be derived.
  • the first feature amount T tm is the thickness target value T t and the thickness measurement value T m of the most driving side point among the points of 5 points or more.
  • the second feature amount T t-s is defined by the deviation between the thickness target value T t and the thickness measurement value T s of the most operating point among the five or more points. ..
  • the embodiment may be specified by the following items.
  • First compression mechanism (41) capable of adding A load in a direction in which the first pressure roller (11) and the second pressure roller (12) are close to at least one of the second main bearing portion (22) and the fourth main bearing portion (24).
  • Second compression mechanism (42) capable of adding A load in the direction in which the first pressure roller (11) and the second pressure roller (12) are separated from each other on at least one of the first bend bearing portion (31) and the third bend bearing portion (33).
  • 1st bend mechanism (51) capable of adding A load in the direction in which the first pressurizing roller (11) and the second pressurizing roller (12) are separated from each other on at least one of the second bend bearing portion (32) and the fourth bend bearing portion (34).
  • 2nd bend mechanism (52) capable of adding Calculation units (815, 816) that calculate the set 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 unit (815, 816) When, Based on the set value calculated by the calculation unit (815, 816), the first compression mechanism (41), the second compression mechanism (42), the first bend mechanism (51), and the second A control unit (817, 818) for controlling the load of the bend mechanism (52), respectively, is provided.
  • the calculation unit (815, 816) has the first compression mechanism (41) and the above so that the change in the thickness of the electrode plate (2) according to the speed change of the transport line of the electrode plate (2) becomes small. Change the set value of the second compression mechanism (42) in advance. Roll press device (1).
  • the calculation unit (815, 816) also determines the relationship between the speed change amount of the line derived in advance and the thickness change amount of the electrode plate (2), and the set acceleration or deceleration of the line. Then, the amount of change in the thickness of the electrode plate (2) after a predetermined time from the start of acceleration or deceleration of the line is predicted.
  • the control unit (817, 818) has the first compression mechanism (41) and the second compression mechanism so that the amount of change in the thickness of the electrode plate (2) during the acceleration period or the deceleration period of the line becomes zero.
  • Control (42) The roll press device (1) according to item 1.
  • the first compression mechanism (41) and the second compression are based on the relationship between the amount of change in the speed of the transfer line and the amount of change in the thickness of the electrode plate (2) and the acceleration or deceleration of the transfer line.
  • feedforward controlling the mechanism (42) it is possible to suppress a change in the thickness of the electrode plate (2) during the acceleration period or the deceleration period of the transport line with high accuracy.
  • the calculation unit (815, 816) is a previously derived amount of change in the load generated by the first compression mechanism (41) and the second compression mechanism (42), and a change in the thickness of the electrode plate (2). Based on the relationship with the amount, the set values of the first compression mechanism (41) and the second compression mechanism (42) so that the thickness change amount during the acceleration period or deceleration period of the line becomes zero. To correct, The roll press device (1) according to item 2.
  • the first compression mechanism is based on the relationship between the amount of change in the load generated by the first compression mechanism (41) and the second compression mechanism (42) and the amount of change in the thickness of the electrode plate (2).
  • the first compression mechanism (41) includes a cylinder (41a) for the first press.
  • the second compression mechanism (42) includes a cylinder (42a) for a second press.
  • the calculation unit (815, 816) is used for the first press during the acceleration period or deceleration period of the line so that the amount of change in the thickness of the electrode plate (2) during the acceleration period or deceleration period of the line becomes zero. Corrects the set values of the pressure of the cylinder (41a) and the pressure of the cylinder (42a) for the second press.
  • the roll press device (1) according to item 3.
  • the thickness change of the electrode plate (2) during the acceleration period or deceleration period of the transport line is increased. It can be suppressed to accuracy.
  • the first compression mechanism (41) includes a cylinder (41a) for the first press.
  • the second compression mechanism (42) includes a cylinder (42a) for a second press.
  • the calculation unit (815, 816) is used for the first press during the acceleration period or deceleration period of the line so that the amount of change in the thickness of the electrode plate (2) during the acceleration period or deceleration period of the line becomes zero. Corrects the set values of the position of the cylinder (41a) and the position of the cylinder (42a) for the second press.
  • the roll press device (1) according to item 3.
  • the thickness change of the electrode plate (2) during the acceleration period or deceleration period of the transport line is increased. It can be suppressed to accuracy.
  • the first compression mechanism (41) further includes a first magnet scale (41c) for measuring the position of the cylinder (41a) for the first press.
  • the second compression mechanism (42) further includes a second magnet scale (42c) for measuring the position of the cylinder (42a) for the second press.
  • the control unit (817d, 818) The position of the cylinder (41a) for the first press measured by the first magnet scale (41c) and the position of the cylinder (41a) for the first press supplied from the calculation unit (815, 816).
  • the pressure of the cylinder (41a) for the first press is controlled so that The position of the cylinder (42a) for the second press measured by the second magnet scale (42c) and the position of the cylinder (42a) for the second press supplied from the calculation unit (815, 816).
  • the pressure of the cylinder (42a) for the second press is controlled so that The roll press device (1) according to item 5.
  • the position of the cylinder (41a) for the first press and the position of the cylinder (42a) for the second press are highly accurate using the first magnet scale (41c) and the second magnet scale (42c). It is possible to realize feedforward control of a compression mechanism with high responsiveness.
  • the first compression mechanism (41) includes a first electric screw (41b).
  • the second compression mechanism (42) includes a second electric screw (42b).
  • the calculation unit (815, 816) uses the first electric screw during the acceleration period or deceleration period of the line so that the amount of change in the thickness of the electrode plate (2) during the acceleration period or deceleration period of the line becomes zero. Correct the set values of the position of (41b) and the position of the second electric screw (42b).
  • the roll press device (1) according to item 3.
  • the first electric screw By feedforward controlling the position of the second electric screw (42b) and the position of the second electric screw (42b), it is possible to suppress the change in the thickness of the electrode plate (2) during the acceleration period or the deceleration period of the transport line with high accuracy.
  • the first main bearing portion (21) and the second main bearing portion (22) provided on one side and the other side of the rotation shaft of the first pressure roller (11) and rotatably support the rotation shaft.
  • the third main bearing portion (23) and the fourth main bearing portion (24) provided on one side and the other side of the rotating shaft of the second pressure roller (12) and rotatably support the rotating shaft.
  • the first bend bearing portion (31) and the second bend bearing portion (32) provided on one side and the other side of the rotation shaft of the first pressure roller (11) and rotatably support the rotation shaft.
  • First compression mechanism (41) capable of adding A load in a direction in which the first pressure roller (11) and the second pressure roller (12) are close to at least one of the second main bearing portion (22) and the fourth main bearing portion (24).
  • Second compression mechanism (42) capable of adding A load in the direction in which the first pressure roller (11) and the second pressure roller (12) are separated from each other on at least one of the first bend bearing portion (31) and the third bend bearing portion (33).
  • 1st bend mechanism (51) capable of adding A load in the direction in which the first pressurizing roller (11) and the second pressurizing roller (12) are separated from each other on at least one of the second bend bearing portion (32) and the fourth bend bearing portion (34).
  • 2nd bend mechanism (52) capable of adding The control device (80) used in the roll press device (1) including the above.
  • Calculation units (815, 816) that calculate the set values of the first compression mechanism (41), the second compression mechanism (42), the first bend mechanism (51), and the second bend mechanism (52).
  • a control unit (817, 818) for controlling the load of 52) is provided.
  • the calculation unit (815, 816) has the first compression mechanism (41) and the above so that the change in the thickness of the electrode plate (2) according to the speed change of the transport line of the electrode plate (2) becomes small. Change the set value of the second compression mechanism (42) in advance. Control device (80).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Electrochemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Press Drives And Press Lines (AREA)
  • Control Of Metal Rolling (AREA)
  • Battery Electrode And Active Subsutance (AREA)
PCT/JP2020/042737 2020-01-09 2020-11-17 ロールプレス装置、及び制御装置 Ceased WO2021140747A1 (ja)

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CN202080092127.4A CN114929463B (zh) 2020-01-09 2020-11-17 辊压装置以及控制装置
US17/791,820 US12580172B2 (en) 2020-01-09 2020-11-17 Roll press device, and control device
JP2021569743A JP7557790B2 (ja) 2020-01-09 2020-11-17 ロールプレス装置、及び制御装置

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2024024214A (ja) * 2022-08-09 2024-02-22 トヨタ自動車株式会社 電極の製造方法
EP4266289A4 (en) * 2021-11-30 2024-11-13 LG Energy Solution, Ltd. ROLLER PRESS SIMULATION DEVICE AND SECONDARY BATTERY PRODUCTION METHOD
EP4224544B1 (en) * 2021-09-28 2025-12-31 Contemporary Amperex Technology (Hong Kong) Limited PRESSURE REGULATION METHOD FOR COLD PRESS AND ELECTRONIC DEVICE
JP2026507984A (ja) * 2022-12-23 2026-03-09 エルジー エナジー ソリューション リミテッド 電極を圧延する方法

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116060453B (zh) * 2023-04-06 2023-08-01 惠州亿纬动力电池有限公司 一种电极极片厚度控制方法及控制系统
KR102886048B1 (ko) * 2023-11-01 2025-11-14 주식회사 엘지에너지솔루션 전극 제조장치 및 그 세팅방법
WO2025095713A1 (ko) * 2023-11-01 2025-05-08 주식회사 엘지에너지솔루션 전극 제조장치 및 그 세팅방법
KR20250146793A (ko) * 2024-04-02 2025-10-13 에스케이온 주식회사 전극 제조 디바이스 및 전극 제조 방법

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6411010A (en) * 1987-07-02 1989-01-13 Kawasaki Steel Co Shape control method for rolled stock in continuous rough rolling
JPH04367309A (ja) * 1991-06-12 1992-12-18 Sumitomo Metal Ind Ltd 板厚制御方法
JPH0638961B2 (ja) * 1984-12-03 1994-05-25 株式会社日立製作所 圧延材の形状制御方法
JP2960011B2 (ja) * 1995-11-24 1999-10-06 古河電気工業株式会社 圧延における加減速時の板厚制御方法および制御装置
JP2014042923A (ja) * 2012-08-27 2014-03-13 Hitachi Power Solutions Co Ltd ロールプレス機及びロールプレス方法
JP2016064441A (ja) * 2014-09-26 2016-04-28 日本電気株式会社 加圧装置及び加圧方法、演算制御装置、並びにコンピュータ・プログラム
JP2016115406A (ja) * 2014-12-11 2016-06-23 株式会社日立パワーソリューションズ 厚み計及びそれを備えるロールプレス機
WO2020100561A1 (ja) * 2018-11-13 2020-05-22 パナソニックＩｐマネジメント株式会社 ロールプレス装置、及び制御装置

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3603124A (en) * 1968-05-09 1971-09-07 Nippon Kokan Kk Computer control system for rolling metal strips using feed-forward and prediction
US5101650A (en) * 1990-05-01 1992-04-07 Allegheny Ludlum Corporation Tandem mill feed forward gage control with speed ratio error compensation
US5613390A (en) * 1993-11-24 1997-03-25 Kawasaki Steel Corporation Corner reduction device equipped with corner rolls, control device thereof, and method of rolling by using these devices
JP3320974B2 (ja) 1996-04-26 2002-09-03 三菱電機株式会社 可逆式圧延機の板厚制御装置
JP3249417B2 (ja) * 1997-02-24 2002-01-21 株式会社日立製作所 圧延機および圧延方法
JP3966393B2 (ja) * 1997-11-07 2007-08-29 富士通株式会社 情報処理装置の盗難防止機構
KR100363413B1 (ko) * 1998-10-27 2003-02-19 주식회사 포스코 압연라인의 판금두께제어방법_
JP4852846B2 (ja) * 2004-12-24 2012-01-11 大日本印刷株式会社 プレスロール装置およびプレス方法
JP4698334B2 (ja) * 2005-05-23 2011-06-08 東芝機械株式会社 シート成形装置およびシート成形装置のロール間隙制御方法
JP5003492B2 (ja) * 2006-08-03 2012-08-15 東芝三菱電機産業システム株式会社 圧延ロール用電動機の駆動装置
CN101795786B (zh) * 2007-09-20 2012-09-26 东芝三菱电机产业系统株式会社 板厚控制装置
JP5328876B2 (ja) * 2011-12-01 2013-10-30 株式会社日立パワーソリューションズ ロールプレス設備
JP5383941B2 (ja) * 2013-05-28 2014-01-08 京セラドキュメントソリューションズ株式会社 Ｉｈ定着装置
JP5801464B1 (ja) * 2014-12-03 2015-10-28 株式会社日立パワーソリューションズ ロールプレス設備
US10933616B2 (en) * 2016-08-01 2021-03-02 Sintokogio, Ltd. Roll press method and roll press system

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0638961B2 (ja) * 1984-12-03 1994-05-25 株式会社日立製作所 圧延材の形状制御方法
JPS6411010A (en) * 1987-07-02 1989-01-13 Kawasaki Steel Co Shape control method for rolled stock in continuous rough rolling
JPH04367309A (ja) * 1991-06-12 1992-12-18 Sumitomo Metal Ind Ltd 板厚制御方法
JP2960011B2 (ja) * 1995-11-24 1999-10-06 古河電気工業株式会社 圧延における加減速時の板厚制御方法および制御装置
JP2014042923A (ja) * 2012-08-27 2014-03-13 Hitachi Power Solutions Co Ltd ロールプレス機及びロールプレス方法
JP2016064441A (ja) * 2014-09-26 2016-04-28 日本電気株式会社 加圧装置及び加圧方法、演算制御装置、並びにコンピュータ・プログラム
JP2016115406A (ja) * 2014-12-11 2016-06-23 株式会社日立パワーソリューションズ 厚み計及びそれを備えるロールプレス機
WO2020100561A1 (ja) * 2018-11-13 2020-05-22 パナソニックＩｐマネジメント株式会社 ロールプレス装置、及び制御装置

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4224544B1 (en) * 2021-09-28 2025-12-31 Contemporary Amperex Technology (Hong Kong) Limited PRESSURE REGULATION METHOD FOR COLD PRESS AND ELECTRONIC DEVICE
EP4266289A4 (en) * 2021-11-30 2024-11-13 LG Energy Solution, Ltd. ROLLER PRESS SIMULATION DEVICE AND SECONDARY BATTERY PRODUCTION METHOD
JP2024024214A (ja) * 2022-08-09 2024-02-22 トヨタ自動車株式会社 電極の製造方法
JP7687304B2 (ja) 2022-08-09 2025-06-03 トヨタ自動車株式会社 電極の製造方法
JP2026507984A (ja) * 2022-12-23 2026-03-09 エルジー エナジー ソリューション リミテッド 電極を圧延する方法

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JPWO2021140747A1 (https=) 2021-07-15

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