WO2006101156A1 - Machine-outil hydraulique, presse-plieuse hydraulique et procédé de commande de celles-ci - Google Patents

Machine-outil hydraulique, presse-plieuse hydraulique et procédé de commande de celles-ci Download PDF

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Publication number
WO2006101156A1
WO2006101156A1 PCT/JP2006/305801 JP2006305801W WO2006101156A1 WO 2006101156 A1 WO2006101156 A1 WO 2006101156A1 JP 2006305801 W JP2006305801 W JP 2006305801W WO 2006101156 A1 WO2006101156 A1 WO 2006101156A1
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WO
WIPO (PCT)
Prior art keywords
hydraulic
pump
motor
control means
pump motor
Prior art date
Application number
PCT/JP2006/305801
Other languages
English (en)
Japanese (ja)
Inventor
Hiroyuki Kojima
Original Assignee
Komatsu Industries Corporation
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 Komatsu Industries Corporation filed Critical Komatsu Industries Corporation
Publication of WO2006101156A1 publication Critical patent/WO2006101156A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q5/00—Driving or feeding mechanisms; Control arrangements therefor
    • B23Q5/22—Feeding members carrying tools or work
    • B23Q5/26—Fluid-pressure drives
    • B23Q5/266—Fluid-pressure drives with means to control the feed rate by controlling the fluid flow
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means
    • B21D5/0209—Tools therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D15/00—Shearing machines or shearing devices cutting by blades which move parallel to themselves
    • B23D15/12—Shearing machines or shearing devices cutting by blades which move parallel to themselves characterised by drives or gearings therefor
    • B23D15/14—Shearing machines or shearing devices cutting by blades which move parallel to themselves characterised by drives or gearings therefor actuated by fluid or gas pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/18—Control arrangements for fluid-driven presses controlling the reciprocating motion of the ram
    • B30B15/20—Control arrangements for fluid-driven presses controlling the reciprocating motion of the ram controlling the speed of the ram, e.g. the speed of the approach, pressing or return strokes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q2705/00—Driving working spindles or feeding members carrying tools or work
    • B23Q2705/10—Feeding members carrying tools or work
    • B23Q2705/12—Fluid-pressure drives

Definitions

  • Hydraulic processing machine hydraulic press brake and control method thereof
  • the present invention relates to a hydraulic processing machine such as a hydraulic press brake or a hydraulic shear that moves a working mechanism for performing a machining operation with hydraulic pressure, and a control method thereof.
  • Patent Document 1 Utility Model Registration No. 2551541
  • Patent Document 2 Japanese Patent Laid-Open No. 9-76022
  • Patent Document 3 Japanese Patent Laid-Open No. 2000-271651
  • Patent Document 4 Japanese Patent Laid-Open No. 10-249440
  • Patent Document 1 stands by with the pump motor rotating while the movable table is not moving up and down, and consumes unnecessary power accordingly. Further, according to the control described in Patent Document 2 or 3, the pump motor is automatically stopped when the movable table has been stopped longer than a certain set time. However, useless power is consumed until the set time is reached, and there is also annoyance that an operation by the operator is required to restart the pump motor.
  • Patent Document 4 discloses a technique for detecting the power frequency and controlling the operation speed of the pump motor in accordance with the power frequency in view of the fact that the power frequency varies depending on the region, for example, 60 Hz or 50 Hz. Yes.
  • this control technology does not contribute to solving the above-mentioned wasteful power consumption and problems.
  • an object of the present invention is to reduce wasteful power consumption in a hydraulic circuit and improve energy efficiency in a hydraulic calorie machine such as a hydraulic press brake or a hydraulic shear. is there.
  • the movement of the working mechanism is controlled by controlling the flow rate of the working oil between the hydraulic pump and the hydraulic actuator by the control valve, and the rotational speed of the pump motor is controlled.
  • the flow rate of hydraulic oil discharged from the hydraulic pump is controlled.
  • the rotational speed of the pump motor is controlled according to whether or not the working mechanism is stationary in a no-load state.
  • the pump motor is stopped when the working mechanism is stationary with no load, while the pump motor is rotated when the working mechanism is powered or stationary with load.
  • the “load state” means a state in which the working mechanism applies a force for the carriage to the workpiece.
  • “Loaded state” means a state in which the working mechanism does not apply a machining force to the workpiece.
  • the rotational speed of the pump motor is controlled in accordance with the flow rate of hydraulic oil supplied from the hydraulic pump to the hydraulic actuator through the control valve.
  • the rotational speed of the pump motor is controlled stepwise or continuously so that the larger the flow rate of hydraulic oil supplied to the hydraulic actuator through the control valve, the higher the rotational speed of the pump motor.
  • the rotational speed of the pump motor is such that the hydraulic pump discharges a minimum flow rate necessary to ensure the flow rate and pressure of hydraulic oil to be supplied to the hydraulic actuator through the control valve. Is controlled. As a result, the flow rate of the hydraulic oil discharged from the hydraulic pump and wastefully returned to the hydraulic oil tank is minimized, and wasteful power consumption is reduced.
  • the motor rotation speed control means further controls the pump motor to control the discharge pressure from the hydraulic pump.
  • the pump motor is controlled so that the hydraulic pump discharges hydraulic oil at a higher pressure than when it is not. By controlling the discharge pressure of the hydraulic pump, the working mechanism can output a force required for machining.
  • An AC electric motor such as a three-phase induction motor can be adopted as the pump motor, and a variable frequency AC power generation circuit such as an inverter is connected to the pump motor in order to vary the rotation speed.
  • a variable frequency AC power generation circuit such as an inverter is connected to the pump motor in order to vary the rotation speed.
  • the present invention is not limited to this, and a motor in which a rotation speed control circuit is inserted, such as a servo motor, may be used as a pump motor.
  • a combination of the AC electric motor and the variable frequency AC power generation circuit as described above is used, and the variable frequency AC power generation circuit includes a quotient.
  • the one whose output frequency can be varied from a frequency lower than the power supply wave number to a higher frequency is used.
  • the general design of conventional processing machines is based on the assumption that an AC electric motor as a pump motor rotates at the commercial power frequency.
  • the rotation of the pump motor is compared with a processing machine with a conventional general design. Since the number can be changed from a lower number of rotations to a higher number of rotations, wasteful noise can be saved and work efficiency can be improved.
  • a hydraulic press brake that moves a movable table hydraulically includes a hydraulic actuator that moves the movable table, a hydraulic pump that discharges hydraulic oil, and a hydraulic pump and a hydraulic actuator.
  • a control valve that controls the flow rate of hydraulic fluid flowing through the pump, a pump motor that drives the hydraulic pump, the rotation speed of which can be variably controlled, a motor rotation speed control means that controls the rotation speed of the pump motor, and a control valve Working mechanism operation control means for controlling the movement of the working mechanism.
  • the work mechanism operation control means stops the movable table in an unloaded state, then lowers the movable table in an unloaded state, then lowers the movable table in a loaded state, and then unloads the movable table.
  • the movement of the movable table is controlled by the procedure of raising in the state.
  • the motor rotation speed control means stops the pump motor when the movable table is stationary with no load, and rotates the pump motor when the movable table is lowered or raised.
  • the rotational speed of the pump motor is controlled to a lower rotational speed than when the movable table is lowered with a load.
  • the number of rotations of the pump motor is variably controlled according to the lifting speed and pressure of the movable table, which varies depending on the bending work scene, and the hydraulic pump is necessary for the work.
  • the hydraulic fluid can be discharged at a flow rate and pressure that can be reduced, and the flow rate of the hydraulic fluid returned to the hydraulic oil tank can be reduced more than before. Thus, energy efficiency is improved.
  • the hydraulic oil discharged from the hydraulic pump is supplied to the hydraulic actuator through the control valve to control the hydraulic processing machine that moves the working mechanism.
  • the control method includes a step of controlling the rotational speed of the hydraulic pump and a step of controlling the movement of the working mechanism by controlling the control valve.
  • FIG. 1 is a diagram showing an overall configuration of a hydraulic press brake according to an embodiment of the present invention.
  • FIG. 2 is a block diagram showing the control functions of the press brake 30, particularly the control functions for controlling the operation of the ram 1.
  • FIG. 3A—FIG. 3B shows the position of ram 1 and the hydraulic pump when the press brake 30 is in the standby state, the bending operation is started, and the bending operation is completed and returned to the standby state again.
  • the time chart which illustrates the change of 14 discharge flow rates and discharge pressure, respectively.
  • Control valve (servo valve, etc.)
  • FIG. 1 shows an overall configuration of a hydraulic cutting machine, for example, a hydraulic press brake, that works according to an embodiment of the present invention.
  • the hydraulic press brake 30 includes a movable table (hereinafter referred to as “ram”) 1 and a fixed table (hereinafter referred to as “table”) 2 as work mechanisms for performing processing operations.
  • ram movable table
  • table fixed table
  • the fixed table 2 is fixed on the floor, and the left and right side frames 6, 6 are fixed to the fixed table 2.
  • the left and right hydraulic cylinders 11 and 11 are attached to the side frames 6 and 6, and the ram 1 is attached to the hydraulic cylinders 11 and 11.
  • the ram 1 can be moved up and down by the action of the hydraulic cylinders 11 and 11.
  • the upper die 3 is fixed to the lower surface of the ram 1, and the lower die 4 is fixed to the upper surface of the table 2.
  • the lower mold 4 provides a V-shaped groove
  • the upper mold 3 provides a V-shaped protrusion that fits into the V-shaped groove of the lower mold 4.
  • Control valves 12 and 12 are connected to the hydraulic cylinders 11 and 11, respectively, and the control valves 12 and 12 are connected to a hydraulic oil tank 13 and a hydraulic oil pump 14, respectively.
  • the hydraulic oil pump 14 also draws hydraulic oil into the hydraulic oil tank 13 and applies pressure to discharge it.
  • the hydraulic oil discharged from the hydraulic oil pump 14 is supplied to the left and right control valves 12 and 12, and the hydraulic oil discharged from the control valves 12 and 12 returns to the hydraulic oil tank 13.
  • Each of the control valves 12 and 12 is, for example, a servo valve, operates in response to a control signal from the controller 23, and supplies hydraulic oil supplied to the hydraulic cylinders 11 and 11. Control flow and pressure. By controlling the flow rate and pressure of the hydraulic oil by the control valves 12 and 12, the position of the ram 1, the raising / lowering speed and the applied pressure are controlled.
  • the hydraulic oil pump 14 is coupled to the pump motor 15 and is driven by the pump motor 15.
  • the hydraulic oil pump 14 is, for example, a constant capacity pump, and the flow rate of hydraulic oil discharged from the hydraulic oil pump 14 is proportional to the rotational speed of the pump motor 15.
  • the pump motor 15 is a three-phase induction motor and is driven by the three-phase AC power supplied from the inverter 24.
  • the inverter 24 receives AC power of, for example, 50 Hz or 60 Hz as commercial power supply (not shown), and rectifies the power to perform orthogonal transformation to output AC power having a required frequency.
  • the frequency of the output AC power of the inverter 24 is variable, and the variable range extends from the frequency power of the commercial power supply (eg 50 Hz or 60 Hz) to the higher frequency.
  • the inverter 24 is connected to the controller 23 and variably controls its output frequency and output voltage in accordance with instructions from the controller 23. By controlling the output frequency of the inverter 24, the rotational speed of the pump motor 15 is variably controlled, and thus the flow rate of the hydraulic oil discharged from the hydraulic oil pump 14 is variably controlled.
  • the output power of the inverter 24 is variably controlled, and the output torque of the pump motor 15 is variably controlled, so that the pressure of the hydraulic oil discharged from the hydraulic oil pump 14 is controlled. Is variably controlled.
  • An NC device 22 is connected to the controller 23.
  • the NC device 22 inputs bending condition data indicating the bending condition of the workpiece 5 from the outside, and based on the bending condition data !, various control axes including the lifting axis of the ram 1 are controlled.
  • the target position and target operation speed are calculated at each time point until the starting force and end of the bending work, and the target position and operation speed at each calculated time point are transferred to the controller 23.
  • the NC device 22 can receive the target position and time of each of the various control axes by manual input from the operator. Set the target operating speed and transfer them to the controller 23.
  • the controller 23 is also connected to a start switch 25, an operation switch 26, and a lift switch 27.
  • the activation switch 25 is, for example, a hand switch that is operated by an operator's hand, while the driving switch 26 and the lift switch 27 are both foot switches that are operated, for example, by an operator.
  • the activation switch 25 gives an activation signal for requesting activation of the press brake 30 to the controller 23 when it is pressed.
  • the operation switch 26 When the operation switch 26 is stepped on, the operation switch 26 gives an operation signal to the controller 23 for requesting execution of the bending operation.
  • the rise switch when it is stepped on, provides the controller 23 with a rise signal requesting that ram 1 be raised to the upper limit position.
  • the controller 23 is constituted by, for example, a computer and an electronic circuit attached thereto, and controls the operation of various control shaft mechanisms including the raising and lowering operation of the ram 1.
  • the controller 23 variably controls the output frequency and output voltage of the inverter 24 and the state of the control valves 12 and 12, thereby controlling the position of the ram 1, the elevating speed and the pressurizing force.
  • FIG. 2 shows the control function of the press brake 30, particularly the control function for controlling the operation of the ram 1.
  • the pump rotation speed control unit 41 receives a motor rotation speed operation command that requests an operation of adjusting the rotation speed of the pump motor 15 from the ram operation control unit 43, and based on the motor rotation speed operation command, the target rotation of the pump motor 15
  • the motor speed command for determining the number and commanding the target speed is output to the inverter 24.
  • the inverter 24 receives the motor rotation speed command from the rotation speed control unit 41, and also receives feedback of the actual rotation speed from the pump motor 15, and receives the motor rotation speed command according to the closed loop control method.
  • the output frequency and output voltage of the inverter 24 are controlled so that the actual speed matches the commanded target speed.
  • the rotational speed of the pump motor 15 is controlled so as to be substantially proportional to the output frequency of the inverter 24, and consequently, the discharge flow rate of the hydraulic pump 14 is controlled. At that time, it is supplied to the pump motor 15 by controlling the output voltage of the inverter 24.
  • the magnitude of the electric power is controlled, so that the torque necessary for the pump motor 15 to rotate at the target rotational speed is secured, and as a result, the control hydraulic pump 14 required to discharge the hydraulic oil at a desired flow rate is secured. A discharge pressure is ensured.
  • the ram operation control unit 43 of the controller 23 receives the pulse signals output from the left and right linear encoders 21 and 21 as the ram 1 moves and counts the position of the ram 1 by counting the pulse signals. Detecting and calculating the ram 1 position by calculating the time change of the ram 1 position.
  • the ram motion control unit 43 receives data indicating a ram motion pattern that defines the target position and the target lifting speed of the ram 1 at each time point from the start to the end of the bending work from the NC device 22. Then, the ram motion control unit 43 uses the closed loop control method to set the target position and target defined by the ram 1 actual position, the lifting speed, and the ram motion pattern from the NC unit 22 at each time of bending work.
  • the left and right control valves 12 and 12 are controlled so as to match the ascending / descending speed, and a motor rotation speed operation command is output to the pump motor rotation speed control unit 23 described above.
  • the rotational speed of the pump motor 15 is controlled in accordance with the motor rotational speed operation command, thereby controlling the discharge flow rate of the hydraulic oil from the hydraulic pump 14 and securing the discharge flow rate.
  • the discharge pressure required for this is also controlled.
  • the flow rate of the hydraulic fluid supplied from the hydraulic pump 14 to the left and right hydraulic cylinders 11 is controlled by the control valves 12 and 12, whereby the hydraulic cylinders 11 and 11 are operated to The ram operation pattern will be followed.
  • the controller 23 performs the output frequency control of the inverter 24 (in other words, the rotational speed control of the pump motor 15 or the discharge flow rate control of the hydraulic pump 14), and the control valves 12, 12 By controlling, the operation of ram 1 is controlled to the target ram operation pattern.
  • the control valves 12 and 12 are controlled such that the lower the target lifting speed of the ram 1 is, the smaller the flow rate of hydraulic oil supplied to the hydraulic cylinder 11 is.
  • the output frequency of the inverter 24 (in other words, the rotational speed of the pump motor 15) is controlled so that the discharge flow rate of the gas becomes small.
  • the hydraulic pump 1 4 can be adjusted in accordance with the rough change in the flow rate of hydraulic oil that needs to be supplied to the hydraulic cylinders 12 and 12.
  • the discharge flow rate is roughly variably controlled, which requires hydraulic cylinders 12 and 12.
  • the hydraulic fluid flow is secured.
  • the flow rate of the hydraulic oil supplied to the hydraulic cylinders 12 and 12 is controlled with high accuracy so that the operation of the ram 1 can accurately follow the target operation pattern by controlling the control valves 12 and 12. Is done.
  • the remainder excluding the amount supplied to the hydraulic cylinders 12 and 12 is returned from the hydraulic pump 14 to the hydraulic tank 13.
  • the hydraulic tank 13 Since the discharge flow rate of the hydraulic pump 14 is variably controlled according to the flow rate required by the hydraulic cylinders 12 and 12, the hydraulic tank 13 is compared to the case where the discharge flow rate of the hydraulic pump 14 is constant as in the prior art. The excess flow returned to is small. Therefore, the wasteful power discarded as wasteful heat is small and the amount of heat generated is small, so the hydraulic tank 13 can be small.
  • FIG. 3A shows an example of a change in the position of the ram 1 from when the press brake 30 enters the standby state, the bending work starts, and after the bending work ends and returns to the standby state.
  • FIG. 3B and FIG. 3C show examples of changes in the discharge flow rate and discharge pressure of the hydraulic pump 14.
  • press brake 30 is in a standby state, and ram 1 is stationary with no load.
  • the controller 23 By controlling the control valves 12 and 12, the hydraulic oil flow to the hydraulic cylinders 11 and 11 is controlled to zero, and the ram 1 is stationary at the upper limit position as shown in FIG. 3A.
  • the inverter 24 does not output power and the pump motor 15 is stopped by the control of the inverter 24 by the controller 23, the discharge flow rate and discharge of the hydraulic pump 15 are stopped as shown in FIGS. 3B and 3C. Both pressures are zero.
  • the bending operation is composed of several phases.
  • the first phase is the “Natural Fall Speed Down” phase.
  • the ram 1 is practically unloaded and descends at a predetermined high speed due to its own weight.
  • the controller 23 controls the control valve 12 to control the flow rate of the hydraulic oil flowing out from the rod side of the hydraulic cylinders 11 and 11, thereby controlling the descending speed of the ram 1 according to the operation pattern.
  • the head side of the hydraulic cylinders 11 and 11 sucks the hydraulic oil directly from the hydraulic oil tank 13.
  • the output frequency of the inverter 24 is controlled to a predetermined minimum frequency (for example, 15 Hz).
  • the rotational speed of the pump motor 15 is almost determined by the output frequency of the inverter 24, and the discharge flow rate of the hydraulic pump 14 is determined by the rotational speed of the pump motor 15. Therefore, by controlling the output frequency of the inverter 24 to the minimum frequency, the pump motor 15 rotates at the minimum number of rotations, and as a result, the discharge flow rate of the hydraulic pump 14 becomes a predetermined value as shown in FIG. 3B. Controlled to minimum flow rate. As a result, an extra portion of the discharge flow rate of the hydraulic pump 14 that is returned directly to the hydraulic oil pump 13 is reduced, and wasteful power consumption is suppressed.
  • a predetermined minimum frequency for example, 15 Hz.
  • the output power of the inverter 24 is controlled to a low value.
  • the discharge pressure of the hydraulic pump 15 is determined by a value obtained by dividing the output power of the inverter 24 (that is, the output power of the pump motor 15) by the rotation speed. Therefore, by controlling the output power of the inverter 24 to a low value, as shown in FIG. 3C, the discharge pressure of the hydraulic pump 14 is controlled to a predetermined low pressure value.
  • the output frequency of the inverter 24 is controlled to a frequency corresponding to the pressurization speed (for example, 50 Hz which is about the same as the commercial power supply frequency), and the pump motor 15 has a rotation speed corresponding to the frequency. So that the discharge flow rate of the hydraulic pump 14 is sufficient but not excessive to lower the ram 1 at the pressurization speed! / The flow rate is slightly larger than the flow rate required for lowering. For this reason, of the discharge flow rate of the hydraulic pump 14, the unnecessary amount of wasted power that is returned directly to the hydraulic oil pump 13 is reduced.
  • the pressurization speed for example, 50 Hz which is about the same as the commercial power supply frequency
  • the output power of the inverter 24 is controlled to a large value, so that the discharge pressure of the hydraulic pump 14 is necessary to bend the work piece 5 as shown in FIG. 3C.
  • the pressure for controlling the pressure is high.
  • the operation proceeds to the next "caloric pressure holding" phase.
  • the hydraulic fluid flow in the hydraulic cylinders 11 and 11 is controlled to zero by the control valves 12 and 12, so that the ram 1 stops at the lower limit position as shown in FIG. Hold the state, that is, the state in which the applied pressure is applied to the workpiece 5.
  • the output frequency of the inverter 24 is controlled to a predetermined minimum frequency (for example, 15 Hz), and the rotation speed of the pump motor 15 is reduced to the minimum rotation speed. The flow rate is reduced to the minimum flow rate.
  • the output power of the inverter 24 is controlled to a large value similar to the “pressure lowering” phase, whereby the discharge pressure of the hydraulic pump 14 is increased to a high pressure to maintain a predetermined pressure. Maintained.
  • the flow rate is controlled through the hydraulic oil pressure control valves 12 and 12 discharged from the hydraulic pump 14 and flows into the rod side of the hydraulic cylinders 11 and 11, and as shown in FIG. 3A
  • the ram 1 rises at a predetermined low gradual climb rate with substantially no load.
  • the output frequency of the inverter 24 is controlled to a frequency corresponding to the slow rising speed (for example, 50 Hz which is about the same as the commercial power supply frequency), and the pump motor 15 corresponds to that frequency. Rotational speed, so that the discharge flow rate of the hydraulic pump 14 is sufficient to raise the ram 1 at a slowly rising speed but not too high.
  • the flow rate is slightly larger than the flow rate required to increase the flow rate. For this reason, an unnecessary amount of unnecessary power that is returned directly to the hydraulic oil pump 13 out of the discharge flow rate of the hydraulic pump 14 is suppressed.
  • the force required to raise ram 1 is small compared to the force required to bend workpiece 5, so the output power of inverter 24 is controlled to a small value, which is shown in Figure 3C.
  • the discharge pressure of the hydraulic pump 14 is controlled to a pressure that is low enough to raise the ram 1.
  • the “slow climb” phase is carried out for a short period of time immediately after the ram 1 operation switches to climb, and then the operation moves to the final “fast climb” phase.
  • the hydraulic oil discharged from the hydraulic pump 14 flows into the rods of the cylinders 11 and 11 at a larger flow rate through the hydraulic control valves 12 and 12, and as shown in FIG. 1 rises at a predetermined high speed rise rate under virtually no load condition.
  • the output frequency of the inverter 24 is controlled to a predetermined maximum frequency (for example, 80 Hz) according to the speed of speed increase, and the pump motor 15 has a maximum rotation speed corresponding to the maximum frequency.
  • the output frequency control by the inverter 24 can control the rotation speed of the pump motor 15 without being limited to the commercial power supply frequency
  • the operating speed of the ram 1 related to the commercial power supply frequency can be controlled. Can be controlled as desired.
  • the pump motor can be rotated at a high speed at the higher frequency. Therefore, as represented by the “rapid rise” phase shown in Fig. 3A-Fig. 3C, high hydraulic pressure is not required, but when ram 1 is moved at high speed, rapid approach or rapid separation is performed.
  • the moving speed of the ram 1 can be increased without increasing the rated power of the pump motor 15 by increasing the discharge flow rate of the hydraulic pump 14 by rotating the pump motor 15 at high speed at high speed. Can be increased more than before. As a result, an improvement in production efficiency can be expected.
  • controller power without separately providing a variable frequency AC output circuit such as an inverter is supplied by a command given directly to the pump motor.
  • the number of rotations of the motor may be variably controlled.
  • a hydraulic actuator for moving the working mechanism other types of actuators such as a hydraulic motor may be used instead of the hydraulic cylinder.
  • the present invention can be applied not only to a hydraulic press brake, but also to a hydraulic shear and other types of hydraulic cutting machines.
  • the rotational speed of the pump motor may be controlled steplessly, that is, continuously instead of stepwise as in the above-described embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Presses (AREA)
  • Shearing Machines (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Press Drives And Press Lines (AREA)

Abstract

L'invention concerne une machine-outil hydraulique, telle qu'une presse-plieuse hydraulique et une cisaille, capable d'accroître le rendement énergétique en réduisant le gaspillage d'énergie, et un procédé de commande de la machine-outil et de la presse-plieuse. On fait varier la vitesse de rotation d'un moteur de pompe (moteur à induction triphasé) (15) entraînant une pompe hydraulique (14) au moyen d'un onduleur (24) pour réguler le débit de refoulement de la pompe hydraulique (14) au minimum requis pour le travail de transformation. Quand un coulisseau (1) est à l'arrêt en position haute maximale, le moteur de pompe (15) s'arrête. Quand le coulisseau (1) descend de sa position haute maximale sous l'effet de son propre poids, on fait tourner le moteur de pompe (15) à sa vitesse de rotation la plus faible. Quand le coulisseau (1) exerce une pression sur une pièce de fabrication (5), on fait tourner le moteur de pompe (15) à une vitesse de rotation minimale. Quand on remonte le coulisseau (1), on fait tourner le moteur de pompe (15) à une vitesse de rotation maximale.
PCT/JP2006/305801 2005-03-24 2006-03-23 Machine-outil hydraulique, presse-plieuse hydraulique et procédé de commande de celles-ci WO2006101156A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005-086559 2005-03-24
JP2005086559A JP4916121B2 (ja) 2005-03-24 2005-03-24 油圧式加工機械、油圧式プレスブレーキおよびその制御方法

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WO2006101156A1 true WO2006101156A1 (fr) 2006-09-28

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EP2036711A1 (fr) 2007-09-12 2009-03-18 Trumpf Maschinen Austria GmbH & CO. KG. Dispositif d'entraînement pour une presse à plier
EP2431166A1 (fr) * 2010-09-20 2012-03-21 Bystronic Laser AG Système de commande pour presse de pliage
WO2022146266A1 (fr) * 2020-12-31 2022-07-07 Baykal Maki̇na Sanayi̇ Ve Ti̇caret Anoni̇m Şi̇rketi̇ Structure de poutre supérieure à gaz propulseur dans des presses-plieuses
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JP2013066931A (ja) * 2011-09-26 2013-04-18 Toyota Auto Body Co Ltd プレス装置
TWI449592B (zh) * 2012-04-09 2014-08-21 Prec Machinery Res & Dev Ct Liquid static pressure rotary recharging energy saving device
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CN102717139A (zh) * 2012-05-11 2012-10-10 江苏龙威重型机械有限公司 一种改进的折弯机或剪板机用油缸
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JP5961089B2 (ja) * 2012-10-17 2016-08-02 株式会社アマダホールディングス 油圧式プレスブレーキ
JP6159578B2 (ja) * 2013-05-28 2017-07-05 中村留精密工業株式会社 工作機械の運転方法
KR101617686B1 (ko) * 2015-03-27 2016-05-03 학교법인 김천대학교 환자 맞춤형 정형외과 임플란트 플레이트용 가변형 금형장치
JP6704716B2 (ja) * 2015-11-26 2020-06-03 株式会社モリタ環境テック 切断処理装置及び切断処理装置の運転方法
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JP6561092B2 (ja) * 2017-06-28 2019-08-14 株式会社栗本鐵工所 ベンディングロール
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EP2036711A1 (fr) 2007-09-12 2009-03-18 Trumpf Maschinen Austria GmbH & CO. KG. Dispositif d'entraînement pour une presse à plier
WO2009033199A1 (fr) * 2007-09-12 2009-03-19 Trumpf Maschinen Austria Gmbh & Co. Kg. Dispositif d'entraînement pour presse à cintrer
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CN101835601B (zh) * 2007-09-12 2013-06-26 特鲁普机械奥地利有限公司及两合公司 用于弯曲压力机的驱动装置
EP2431166A1 (fr) * 2010-09-20 2012-03-21 Bystronic Laser AG Système de commande pour presse de pliage
WO2022146266A1 (fr) * 2020-12-31 2022-07-07 Baykal Maki̇na Sanayi̇ Ve Ti̇caret Anoni̇m Şi̇rketi̇ Structure de poutre supérieure à gaz propulseur dans des presses-plieuses
WO2023193035A1 (fr) * 2022-04-05 2023-10-12 Trumpf Maschinen Austria Gmbh & Co. Kg. Machine de formage destinée au façonnage de pièces et procédé associé

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JP2006263872A (ja) 2006-10-05
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CN100515665C (zh) 2009-07-22
KR100940472B1 (ko) 2010-02-04

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