EP1965083B1 - Hydraulische einheit und verfahren zur steuerung der drehzahl eines motors in der hydraulischen einheit - Google Patents

Hydraulische einheit und verfahren zur steuerung der drehzahl eines motors in der hydraulischen einheit Download PDF

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Publication number
EP1965083B1
EP1965083B1 EP07806100A EP07806100A EP1965083B1 EP 1965083 B1 EP1965083 B1 EP 1965083B1 EP 07806100 A EP07806100 A EP 07806100A EP 07806100 A EP07806100 A EP 07806100A EP 1965083 B1 EP1965083 B1 EP 1965083B1
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Prior art keywords
oil pressure
motor
command value
load
current command
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EP07806100A
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English (en)
French (fr)
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EP1965083A1 (de
EP1965083A4 (de
Inventor
Tetsuo Nakata
Junichi Miyagi
Yasuto Yanagida
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Daikin Industries Ltd
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Daikin Industries Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/20—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the driving speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
    • 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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1202—Torque on the axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2203/00—Motor parameters
    • F04B2203/02—Motor parameters of rotating electric motors
    • F04B2203/0201—Current
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2203/00—Motor parameters
    • F04B2203/02—Motor parameters of rotating electric motors
    • F04B2203/0209—Rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/05—Pressure after the pump outlet
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/255—Flow control functions
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. torque or rotational speed
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6656—Closed loop control, i.e. control using feedback

Definitions

  • the present invention relates to an oil pressure unit for driving an oil pressure pump with a motor.
  • a speed control (PI control) calculation is executed to calculate a current command value through comparison of a speed command value of the motor and a current rotation speed, and a current control based on the current command value is realized by an inverter.
  • the motor controlled by the inverter is then driven so that pressure oil is discharged from the oil pressure pump (e.g., patent document 1).
  • Patent document 1 Japanese Laid-Open Patent Publication No. 2004-162860
  • oil pressure the pressure of oil (oil pressure) becomes larger as a total amount of the oil discharged from the oil pressure pump by a drive of the oil pressure pump increases.
  • An increase in the oil pressure leads to an increase in a load of the oil pressure pump in discharge, and causes a load torque of the motor to become larger.
  • a method of preventing lowering of the rotation speed of the motor includes a method of improving a response of the control by shortening a control period of the PI control by improving a processing speed of a microcomputer that performs the PI control.
  • a cost of the microcomputer increases if such method is adopted.
  • the improvement of the processing speed of the microcomputer has physical limitations, lowering in the rotation speed of the motor cannot be effectively prevented with such method.
  • Another method includes a method using the load torque for the speed control in which the load torque is estimated from acceleration information obtained by differentiating the rotation speed of the motor.
  • the rotation speed is discrete information, a noise component increases by differentiation.
  • a behavior will become unstable if the speed control is executed using the load torque.
  • a first aspect of an oil pressure unit relates to the oil pressure unit for supplying oil to an actuator by driving an oil pressure pump (16A) with a motor (15), characterized in that it comprises an inverter (14) for supplying power to the motor (15), a load sensor (17) for detecting a load of the oil pressure pump (16A), a rotation sensor (21) for detecting a rotation speed of the motor (15), a current command value calculation means (12) for calculating a current command value so that a deviation between a speed command value representing a target rotation speed of the motor (15) and a rotation speed of the motor (15) converges to zero, a correction means (18A; ... ; 18D) for correcting the current command value based on the load of the oil pressure pump (16A), and a control signal generation means (13) for outputting a control signal to the inverter (14) based on a corrected current command value.
  • an inverter (14) for supplying power to the motor (15)
  • a load sensor (17) for detecting a load of the oil pressure pump
  • said correction means (18A; ... ;18D) corrects the current command value to raise the rotation speed of said motor (15) with an increase in the load of said oil pressure pump (16A).
  • said correction means (18A; ... ; 18D) increases the current command value with an increase in the load of said oil pressure pump (16A).
  • said correction means (18A) acquires a correction value (Iv) using a correction coefficient (Kf) set in advance, and adds said correction value (Iv) to said current command value.
  • said correction means (18B; 18C; 18D) acquires a correction value (Iv) using a data table DT acquired in advance, and adds said correction value (Iv) to said current command value.
  • said load sensor (17) is a pressure sensor (17) for detecting a pressure of oil in a discharge line (19) of said oil pressure pump (16A).
  • a seventh aspect of the oil pressure unit relates to a speed control method of a motor (15) in the oil pressure unit for supplying oil to an actuator by driving an oil pressure pump (16A) with the motor (15) controlled by an inverter (14) and, characterized in that it comprises the steps of a) detecting a load of said oil pressure pump (16A); b) detecting a rotation speed of said motor (15); c) calculating a current command value so that a deviation between a speed command value representing a target rotation speed of said motor (15) and a rotation speed of said motor (15) converges to zero; d) correcting the current command value based on the load of said oil pressure pump (16A); and e) outputting a control signal to said inverter (14) based on the corrected current command value.
  • the followability of the rotation speed of the motor with respect to the variation of the load (load oil pressure) of the oil pressure pump can be improved since the current command value is corrected based on the load of the oil pressure pump.
  • FIG. 1 is a schematic view showing a configuration of an oil pressure unit 10A according to the embodiment of the present invention.
  • the oil pressure unit 10A is connected to a molding machine etc., and supplies oil as working fluid to an actuator (not shown) having the oil pressure as the power source.
  • the oil pressure unit 10A includes a controller 20, an inverter unit 14, a motor 15, an oil pressure pump 16A, a pressure sensor 17, and a pulse generator 21.
  • the oil is taken in from a tank (not shown) by the oil pressure pump 16A driven by the motor 15, and the oil is discharged.
  • the discharged oil is supplied to the actuator such as an oil pressure cylinder or an oil pressure motor through a discharge line 19.
  • the pressure sensor 17 serves as a load sensor for detecting the load of the oil pressure pump.
  • the pressure sensor 17 also detects the pressure (also referred to as “present pressure” or “load oil pressure”) of the oil in the discharge line 19 of the oil pressure pump.
  • the pulse generator 21 serves as a rotation sensor for outputting a pulse signal for detecting the rotation speed of the motor to the controller 20 (speed detection part 22).
  • the inverter unit 14 controls the rotation number of the motor 15 by performing switching based on a control signal from the controller 20.
  • the controller 20 includes a P-Q control part 11, a current command value calculation part 12, a correction part 18A, a control signal generation part 13, and a speed detection part 22.
  • the controller 20 outputs a control signal for driving the inverter.
  • the P-Q control part 11 generates discharge pressure-discharge flow rate characteristics (P-Q characteristics) based on a set pressure and a set flow rate from a higher level system such as a molding machine.
  • the P-Q control part 11 outputs a speed command value based on the present pressure from the pressure sensor 17 as an input.
  • the current command value calculation part (also referred to as "PI control part") 12 performs a proportional-integral (PI) control with the speed command value and the current speed as inputs, and outputs a current command value. More specifically, the PI control part 12 calculates the current command value so that the deviation between speed command value representing the target rotation speed of the motor 15 and the rotation speed of the motor 15 converges to zero.
  • PI control part also referred to as "PI control part”
  • the correction part 18A corrects the current command value based on the present pressure from the pressure sensor 17. The details will be hereinafter described.
  • the control signal generation part 13 generates a control signal for controlling the inverter part 14 based on the corrected current command value.
  • the correction part 18A will now be described in detail.
  • FIG. 2 is a schematic view showing a configuration of a general oil pressure unit 10B.
  • the oil pressure unit 10B has the same configuration as the oil pressure unit 10A other than that the correction part 18A is not equipped.
  • a high response is demanded on the molding machine to which the oil pressure unit 10B is connected from the standpoint of mass production.
  • a stepwise speed command is provided in a short cycle.
  • the oil pressure (load oil pressure) in the discharge line 19 of the oil pressure pump 16A becomes larger.
  • the load oil pressure becomes larger, the load of the oil pressure pump 16A in discharge increases. That is, the load oil pressure and the load torque of the motor 15 are more or less in a proportional relationship, where the load torque of the motor 15 becomes larger as the load oil pressure becomes larger.
  • the rotation speed of the motor 15 drastically rises in response to the speed command value.
  • the load oil pressure drastically increases with rise in rotation speed of the motor 15.
  • the load torque drastically becomes larger with an increase in the load oil pressure.
  • the speed control by the PI control cannot be followed, and the rotation speed of the motor 15 lowers.
  • the generated torque of the motor 15 needs to become larger with the increase in load torque.
  • the generated torque of the motor 15 and the motor current are in proportional relationship, and thus the motor current, that is, the current command value merely needs to become large for the generated torque of the motor 15 to become large.
  • the followability of the rotation speed of the motor 15 with respect to variation of the load oil pressure can be improved by changing the current command value with variation of the load oil pressure. Furthermore, the lowering in the rotation speed of the motor 15 can be prevented by increasing the current command value with the increase in load oil pressure.
  • the correction part 18A for correcting the current command value based on the load oil pressure is equipped.
  • the correction value (current correction value) Iv is acquired using the present pressure (pressure detected value) Pd detected by the pressure sensor 17 and a correction coefficient Kf acquired in advance.
  • the correction value Iv is added to the current command value output from the current command value calculation part 12.
  • the current command value is corrected based on the load of the oil pressure pump 16A, that is, the pressure (load oil pressure) of the oil in the discharge line 19. Therefore, the followability of the rotation speed of the motor 15 with respect to the variation of the load (load oil pressure) of the oil pressure pump 16A can be enhanced (improved).
  • the coefficient acquired through tests in advance is used as the correction coefficient Kf.
  • the correction coefficient Kf is set so that the current command value necessary for preventing lowering in the rotation speed of the motor 15 and following the speed command can be acquired in the correction part 18A.
  • the correction coefficient Kf can also be represented as being set so that the lack of current command value necessary for preventing lowering in the rotation speed of the motor 15 and following the speed command can be acquired as the correction value.
  • the rotation speed of the motor 15 can be controlled to the rotation speed given by the speed command value.
  • the correction value Iv acquired using the correction coefficient Kf becomes larger with rise in load oil pressure.
  • the current command value can be corrected so as to raise the rotation speed of the motor 15 with the increase in load oil pressure, and lowering in rotation speed of the motor 15 involved in rise of the load oil pressure is prevented.
  • FIG. 3 is a view showing a state of an operation when a stepwise speed command SC is provided in the oil pressure unit 10A according to the present embodiment.
  • the correction value Iv which value becomes larger with the increase in the load oil pressure Pd1 is acquired in the correction part 18A.
  • the correction value Iv is added to the output from the current command value calculation part 12, and the corrected current command value Ic1 is acquired (see FIG. 3(b) ).
  • the current command value Ic1 becomes larger following the increase in the load oil pressure Pd1, and thus the lowering in the rotation speed Rs1 of the motor 15 by the increase in load torque is prevented.
  • the rotation speed Rs1 of the motor 15 thus can follow the rotation speed given by the speed command SC.
  • FIG. 4 is a view showing a state of an operation when the stepwise speed command SC is provided in the oil pressure unit 10B.
  • the magnitude of the current command value is different in zone BT.
  • the difference in magnitude of the current command value indicates that the appropriate current command value necessary for following the rotation speed of the motor 15 to the speed command SC is not acquired (calculated) in the oil pressure unit 10B ( FIG. 4(b) ).
  • the correction value Iv that becomes larger with the increase in the load oil pressure Pd is acquired using the load oil pressure Pd detected by the pressure sensor 17 and the correction coefficient Kf previously acquired in the correction part 18A.
  • the relevant correction value Iv is added to the current command value output from the current command value calculation part 12.
  • the current command value Ic1 can be increased following the increase in the load oil pressure Pd1 by adding the correction value Iv acquired based on the load oil pressure Pd1 to the current command value output from the current command value calculation part 12 in a feedforward manner.
  • the lowering in the rotation speed Rs1 of the motor 15 by the increase in load torque thus can be prevented.
  • FIG. 5 is a schematic view showing an oil pressure unit 10C including a correction part 18B capable of acquiring the correction value Iv using a data table DT.
  • the correction value Iv may be acquired (calculated) using a data table DT showing a relationship between the load oil pressure (pressure detected value) Pd acquired in advance and the correction value Iv in the correction part 18B, as shown in FIG. 5 .
  • An appropriate correction value Iv thus can be acquired with respect to the load pressure Pd from the pressure sensor 17 even if the load pressure and the correction value necessary for following the speed command are not in a proportional relationship.
  • oil pressure unit 10A is driven using one oil pressure pump 16A in the above embodiment, but is not limited thereto.
  • FIG. 6 is a schematic view showing an oil pressure unit 10D in which two oil pressure pumps 16A, 16B are driven with one motor.
  • information indicating which oil pressure pump is being driven is output to the correction part 18C from the P-Q control part 11 according to the switching of the pump when configuring the oil pressure unit 10D with two oil pressure pumps 16A, 16B.
  • the data table for acquiring the correction value Iv is switched according to the pump drive information, and the correction value Iv corresponding to the driven pump is acquired.
  • the data table showing a relationship between the load oil pressure (pressure detected value) Pd and the correction value Iv in a case where the two oil pressure pumps 16A, 16B are simultaneously driven is used to acquire the correction value Iv.
  • FIG. 7 is a schematic view showing an oil pressure unit in which two oil pressure pumps are connected in series. As shown in FIG. 7 , when the two oil pressure pumps are connected in series such that the oil discharged from one oil pressure pump 16B is taken in by the other oil pressure pump 16A, the pressure of the oil discharged form the oil pressure pump 16A on the downstream side is detected by the pressure sensor (17). The current command value is corrected based on the oil pressure discharged by the oil pressure pump 16A on the downstream side.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Computer Hardware Design (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Ac Motors In General (AREA)
  • Control Of Electric Motors In General (AREA)

Claims (4)

  1. Öldruckeinheit zum Bereitstellen von Öl an einen Aktuator durch Antreiben einer Öldruckpumpe (16A) mit einem Motor (15), wobei die Öldruckeinheit aufweist:
    einen Wechselrichter (14) zum Zuführen von elektrischem Strom zum Motor (15);
    einen Kraftsensor (17) zum Erfassen einer Last der Öldruckpumpe (16A);
    einen Rotationssensor (21) zum Erfassen einer Drehzahl des Motors (15);
    ein Strom-Befehlswert-Berechnungsmittel (12) zur Berechnung eines Strom-Befehlswerts, so dass eine Abweichung zwischen einem Drehzahlbefehlswert, der eine Solldrehzahl des Motors (15) darstellt, und einer Drehzahl des Motors (15) gegen Null konvergiert;
    ein Korrekturmittel (18A; ... ; 18D) zum Korrigieren des Strom-Befehlswerts basierend auf der Last der Öldruckpumpe; und
    ein Steuersignal-Erzeugungsmittel (13) zum Ausgeben eines Steuersignals an den Wechselrichter (14) basierend auf einem korrigierten Strom-Befehlswert,
    dadurch gekennzeichnet, dass
    das Korrekturmittel (18B; 18C; 18D) den Strom-Befehlswert erhöht, um eine Drehzahl des Motors (15) nahe der Solldrehzahl zu bewirken bei einem Anstieg der Last der Öldruckpumpe (16A).
  2. Öldruckeinheit nach Anspruch 1, dadurch gekennzeichnet, dass das Korrekturmittel (18A; ... ; 18D) den Strom-Befehlswert korrigiert, um die Drehzahl des Motors (15) mit einem Anstieg der Last der Öldruckpumpe (16A) zu erhöhen.
  3. Öldruckeinheit nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das Korrekturmittel (18A; ... ; 18D) den Strom-Befehlswert mit einem Anstieg der Last der Öldruckpumpe (16A9 erhöht.
  4. Öldruckeinheit nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Lastsensor (17) ein Drucksensor (17) zum Erfassen eines Öldrucks in einer Abflussleitung (19) der Öldruckpumpe (16A) ist
EP07806100A 2006-08-30 2007-08-27 Hydraulische einheit und verfahren zur steuerung der drehzahl eines motors in der hydraulischen einheit Active EP1965083B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006233529A JP4425253B2 (ja) 2006-08-30 2006-08-30 油圧ユニットおよび油圧ユニットにおけるモータの速度制御方法
PCT/JP2007/066559 WO2008026544A1 (fr) 2006-08-30 2007-08-27 Unité hydraulique et procédé permettant de commander la vitesse du moteur dans une unité hydraulique

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JP5884481B2 (ja) * 2011-12-28 2016-03-15 株式会社ジェイテクト モータ制御装置および電動ポンプユニット
EP2664968A1 (de) * 2012-05-16 2013-11-20 Siemens Aktiengesellschaft Regeleinrichtung für eine Hydraulikzylindereinheit mit Einzelventilsteuerung
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JP6050081B2 (ja) * 2012-10-05 2016-12-21 株式会社荏原製作所 ドライ真空ポンプ装置
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JP6396733B2 (ja) * 2014-09-22 2018-09-26 オークマ株式会社 油圧制御装置
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WO2008026544A1 (fr) 2008-03-06
JP4425253B2 (ja) 2010-03-03
KR20080087084A (ko) 2008-09-30
EP1965083A1 (de) 2008-09-03
JP2008057611A (ja) 2008-03-13
US20090097986A1 (en) 2009-04-16
CN101360917B (zh) 2011-12-07
KR100954697B1 (ko) 2010-04-26
CN101360917A (zh) 2009-02-04
EP1965083A4 (de) 2009-11-11
ATE528512T1 (de) 2011-10-15

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