WO2020255391A1 - Dispositif et procédé de commande de moteur, et procédé de conception associé - Google Patents

Dispositif et procédé de commande de moteur, et procédé de conception associé Download PDF

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Publication number
WO2020255391A1
WO2020255391A1 PCT/JP2019/024774 JP2019024774W WO2020255391A1 WO 2020255391 A1 WO2020255391 A1 WO 2020255391A1 JP 2019024774 W JP2019024774 W JP 2019024774W WO 2020255391 A1 WO2020255391 A1 WO 2020255391A1
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WO
WIPO (PCT)
Prior art keywords
motor
operation mode
actuator
value
torque
Prior art date
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PCT/JP2019/024774
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English (en)
Japanese (ja)
Inventor
芳貴 生武
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三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2019/024774 priority Critical patent/WO2020255391A1/fr
Publication of WO2020255391A1 publication Critical patent/WO2020255391A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02P—CONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
    • H02P29/00—Arrangements for regulating or controlling electric motors, appropriate for both AC and DC motors
    • H02P29/40—Regulating or controlling the amount of current drawn or delivered by the motor for controlling the mechanical load

Definitions

  • the present invention relates to a motor control device, a motor control method, and a design method.
  • Patent Document 1 discloses such an actuator.
  • valve system a system that controls the valve opening by a direct acting actuator
  • a direct acting actuator Specifically, for example, valve systems for wastegate valves have been developed.
  • a device for controlling the operation of a rotary motor in a linear actuator hereinafter referred to as a “motor control device” has been developed.
  • Actuators for valve systems include a shaft pushing operation (hereinafter referred to as “pushing operation”), a shaft pulling operation (hereinafter referred to as “pulling operation”), and an operation of holding the position of the shaft with respect to the linear motion direction (hereinafter referred to as “pushing operation”).
  • Pump operation a shaft pushing operation
  • pulling operation a shaft pulling operation
  • pump operation an operation of holding the position of the shaft with respect to the linear motion direction
  • Pisition holding operation is required. That is, the opening degree of the valve changes due to the pushing operation or the pulling operation. On the other hand, the opening of the valve is maintained by the position holding operation.
  • the pushing and pulling operations are collectively referred to as the “pushing and pulling operations”.
  • the thrust force applied to the actuator during the push-pull operation is sometimes referred to as “actuating force”.
  • the thrust force of the actuator during the position holding operation is sometimes referred to as “holding force”.
  • a characteristic indicating a thrust generated by an actuator with respect to a torque generated by a motor may be referred to as a "torque-thrust characteristic”.
  • the operating force required for the actuator is sometimes called “required operating force”.
  • the holding force required for the actuator may be referred to as “required holding force”.
  • the torque output by the motor may be referred to as "output torque”.
  • the frictional force in the feed screw mechanism acts as a negative force for the push-pull operation, that is, a force that hinders the push-pull operation.
  • the frictional force in the feed screw mechanism acts as a positive force for the position holding operation, that is, a force assisting the position holding operation.
  • the torque-thrust characteristic during the position holding operation is different from the torque-thrust characteristic during the push-pull operation. Therefore, it is preferable that the output torque during the position holding operation is set to a different value with respect to the output torque during the push-pull operation by a different setting method. More specifically, if the required holding force is equal to the required operating force, it is preferable that the output torque during the position holding operation is set to a value smaller than the output torque during the push-pull operation. ..
  • the method of setting the output torque during the position holding operation and the method of setting the output torque during the push-pull operation are not separated.
  • the output torque is set based on the torque-thrust characteristic during the push-pull operation regardless of whether the actuator operation is the push-pull operation or the position holding operation. It was a thing. In other words, the output torque was set to a large value from the viewpoint of avoiding the occurrence of insufficient thrust during the push-pull operation. For this reason, there is a problem that an excessive thrust is generated due to an excessive torque generated during the position holding operation. As a result, there is a problem that the power consumption by the motor increases. In addition, there is a problem that a large motor is adopted.
  • the conventional motor control device has a problem that the control accuracy of the motor is low. More specifically, there is a problem that the control accuracy of the output torque is low.
  • the present invention has been made to solve the above problems, and an object of the present invention is to improve the control accuracy of the motor.
  • the motor control device of the present invention is a motor control device for an actuator having a motor and a feed screw mechanism, and the operation mode of the motor corresponds to the first operation mode corresponding to the push-pull operation by the actuator or the position holding operation by the actuator.
  • Mode setting unit that selectively sets the second operation mode, and when the operation mode is set to the first operation mode, the motor is operated in the first operation mode and the operation mode is set to the second operation mode. When this is done, the motor control unit for operating the motor in the second operation mode is provided.
  • the control accuracy of the motor can be improved.
  • FIG. 1 It is a block diagram which shows the state which the motor control device which concerns on Embodiment 1 is provided in a vehicle. It is explanatory drawing which shows the hardware composition of the motor control device which concerns on Embodiment 1. FIG. It is explanatory drawing which shows the other hardware configuration of the motor control device which concerns on Embodiment 1. FIG. It is a flowchart which shows the operation of the motor control device which concerns on Embodiment 1. FIG. It is a flowchart which shows the design method of the motor control device which concerns on Embodiment 1. FIG. It is explanatory drawing which shows the example of the model corresponding to a valve system. It is explanatory drawing which shows the example of the control circuit corresponding to the torque thrust conversion formula.
  • FIG. 1 is a block diagram showing a state in which the motor control device according to the first embodiment is provided in the vehicle.
  • the motor control device according to the first embodiment will be described with reference to FIG. Further, an actuator to be controlled by the motor control device will be described. In addition, a valve system including such an actuator will be described.
  • the vehicle 1 is provided with a wastegate valve 2.
  • the opening degree of the wastegate valve 2 is controlled by the linear actuator 3.
  • the actuator 3 has a rotary motor 4. Further, the actuator 3 has a feed screw mechanism 5.
  • the lead screw mechanism 5 functions as a speed reduction mechanism. As a result, the rotary motion of the rotor (not shown) in the motor 4 is converted into the linear motion of the shaft (not shown) in the actuator 3.
  • a valve body (not shown) of the wastegate valve 2 is provided at the tip of the shaft.
  • the wastegate valve 2 and the actuator 3 form the main part of the valve system 6.
  • the operation of the motor 4 is controlled by the motor control device 100.
  • the operation mode of the motor 4 is divided into the following two types of operation modes. That is, there are two types of operation modes: an operation mode corresponding to the push-pull operation by the actuator 3 (hereinafter referred to as "first operation mode”) and an operation mode corresponding to the position holding operation by the actuator 3 (hereinafter referred to as “second operation mode”). It has been carved.
  • the motor control device 100 will be described below. Further, the upper electronic control unit 7 with respect to the motor control device 100 will be described.
  • the mode setting unit 11 sets the operation mode of the motor 4. More specifically, the mode setting unit 11 selectively sets the operation mode of the motor 4 to the first operation mode or the second operation mode based on the output signal from the electronic control unit 7.
  • the output signal from the electronic control unit 7 indicates the opening degree required for the wastegate valve 2 (hereinafter referred to as "required opening degree").
  • the current opening degree of the wastegate valve 2 (hereinafter referred to as “current opening degree”) is known. Therefore, the mode setting unit 11 calculates a difference value between the required opening degree and the current opening degree, and compares the calculated difference value with a predetermined threshold value. The mode setting unit 11 sets the operation mode of the motor 4 to the first operation mode or the second operation mode according to the result of the comparison.
  • the motor control unit 12 controls the operation of the motor 4 by controlling the amount of energization of the motor 4. More specifically, the motor control unit 12 executes control for operating the motor 4 in the first operation mode when the operation mode of the motor 4 is set to the first operation mode by the mode setting unit 11. is there. Further, the motor control unit 12 operates the motor 4 in the second operation mode when the operation mode of the motor 4 is set to the second operation mode by the mode setting unit 11.
  • the motor control unit 12 has a torque setting unit 13.
  • the torque setting unit 13 sets the output torque of the motor 4 to a value corresponding to the required operating force for the actuator 3. Further, the torque setting unit 13 sets the output torque of the motor 4 to a value corresponding to the required holding force for the actuator 3 when the motor 4 is operated in the second operation mode.
  • the torque setting unit 13 is designed based on the conversion formula (hereinafter referred to as “torque thrust conversion formula”) F1 and F2 between the torque generated by the motor 4 and the thrust generated by the actuator 3.
  • the torque thrust conversion formulas F1 and F2 are a conversion formula corresponding to the push-pull operation (hereinafter referred to as “first torque thrust conversion formula”) F1 and a conversion formula corresponding to the position holding operation (hereinafter referred to as “second torque thrust conversion formula”). “.) It includes F2.
  • the torque setting unit 13 calculates a torque value according to the required operating force based on the first torque thrust conversion formula F1. The torque setting unit 13 sets the output torque of the motor 4 to the calculated value. Further, when the motor 4 is operated in the second operation mode, the torque setting unit 13 calculates a torque value according to the required holding force based on the second torque thrust conversion formula F2. The torque setting unit 13 sets the output torque of the motor 4 to the calculated value.
  • the first torque thrust conversion formula F1 and the second torque thrust conversion formula F2 were derived based on the results of analysis using the model M corresponding to the valve system 6.
  • the method of generating the model M, the method of deriving the first torque thrust conversion formula F1 and the second torque thrust conversion formula F2, the design method of the motor control unit 12, and the like will be described later in the second embodiment.
  • the torque value according to the required operating force can be accurately calculated.
  • the torque value according to the required holding force can be accurately calculated. As a result, the control accuracy of the output torque can be further improved.
  • the main part of the motor control device 100 is composed of the mode setting unit 11 and the motor control unit 12.
  • the motor control device 100 has a processor 21 and a memory 22.
  • a program for realizing the functions of the mode setting unit 11 and the motor control unit 12 is stored in the memory 22.
  • the functions of the mode setting unit 11 and the motor control unit 12 are realized by the processor 21 reading and executing the stored program.
  • the motor control device 100 has a processing circuit 23.
  • the functions of the mode setting unit 11 and the motor control unit 12 are realized by the dedicated processing circuit 23.
  • the motor control device 100 has a processor 21, a memory 22, and a processing circuit 23 (not shown).
  • some of the functions of the mode setting unit 11 and the motor control unit 12 are realized by the processor 21 and the memory 22, and the remaining functions are realized by the dedicated processing circuit 23.
  • the processor 21 is composed of one or a plurality of processors.
  • a CPU Central Processing Unit
  • a GPU Graphics Processing Unit
  • a microprocessor a microcontroller
  • DSP Digital Signal Processor
  • the memory 22 is composed of one or a plurality of non-volatile memories. Alternatively, the memory 22 is composed of one or more non-volatile memories and one or more volatile memories. Each volatile memory uses, for example, a RAM (Random Access Memory).
  • the individual non-volatile memories include, for example, a ROM (Read Only Memory), a flash memory, an EPROM (Erasable Programmable Read Only Memory), an EEPROM (Electrically Erasable Primary Memory) or an EEPROM (Electrically Emergency Memory) Drive) is used.
  • the processing circuit 23 is composed of one or a plurality of digital circuits. Alternatively, the processing circuit 23 is composed of one or more digital circuits and one or more analog circuits. That is, the processing circuit 23 is composed of one or a plurality of processing circuits.
  • the individual processing circuits include, for example, an ASIC (Application Specific Integrated Circuit), a PLD (Programmable Logic Device), an FPGA (Field-Programmable Gate Array), an FPGA (Field-Programmable Gate Array), and a System-System (System) System. ) Is used.
  • the mode setting unit 11 sets the operation mode of the motor 4 (step ST1). Since the specific example of the operation mode setting method is as described above, the description thereof will be omitted again.
  • the motor control unit 12 executes control to operate the motor 4 in the operation mode set in step ST1 (step ST2).
  • the torque setting unit 13 sets the output torque of the motor 4 to a value according to the required operating force or a value according to the required holding force according to the operation mode of the motor 4. Since the specific example of the output torque setting method is as described above, the description thereof will be omitted again.
  • the valve in the valve system 6 is not limited to the wastegate valve 2.
  • the valve system 6 may have any valve as long as the opening degree is controlled by the linear acting actuator 3.
  • the system in which the actuator 3 is used is not limited to the valve system 6.
  • the actuator 3 may be used in any system as long as it is a system in which the linear acting actuator 3 is used.
  • the motor control device 100 is the motor control device 100 for the actuator 3 having the motor 4 and the feed screw mechanism 5, and the operation mode of the motor 4 is pushed and pulled by the actuator 3.
  • the mode setting unit 11 that selectively sets the first operation mode corresponding to the above or the second operation mode corresponding to the position holding operation by the actuator 3, and the motor 4 when the operation mode is set to the first operation mode. It is provided with a motor control unit 12 that operates in one operation mode and operates the motor 4 in the second operation mode when the operation mode is set to the second operation mode. As a result, the control accuracy of the motor 4 can be improved.
  • the motor control unit 12 sets the output torque by the motor 4 to a value corresponding to the required operating force for the actuator 3, and sets the motor 4 in the second operation mode.
  • the output torque is set to a value corresponding to the required holding force for the actuator 3.
  • the motor control unit 12 calculates the value of the output torque according to the required operating force based on the first torque thrust conversion formula F1 corresponding to the push-pull operation, and the second torque thrust conversion formula corresponding to the position holding operation. Calculate the output torque value according to the required holding force based on.
  • the first torque thrust conversion formula F1 the value of the output torque according to the required operating force can be accurately calculated.
  • the second torque thrust conversion formula F2 the torque value according to the required holding force can be accurately calculated. As a result, the control accuracy of the output torque can be further improved.
  • first torque thrust conversion formula F1 and the second torque thrust conversion formula F2 are based on the results of analysis using the model M corresponding to the system (valve system 6) including the actuator 3. As will be described later in the second embodiment, the first torque thrust conversion formula F1 and the second torque thrust conversion formula F2 can be accurately derived by using the model M.
  • the motor control method is a motor control method for an actuator 3 having a motor 4 and a feed screw mechanism 5, and a mode setting unit 11 pushes and pulls the operation mode of the motor 4 by the actuator 3.
  • step ST1 for selectively setting the first operation mode corresponding to the operation or the second operation mode corresponding to the position holding operation by the actuator 3 and the motor control unit 12 set the operation mode to the first operation mode.
  • the motor 4 is operated in the first operation mode, and the step ST2 is provided for operating the motor 4 in the second operation mode when the operation mode is set to the second operation mode.
  • the control accuracy of the motor 4 can be improved.
  • FIG. 4 is a flowchart showing a design method of the motor control device according to the first embodiment.
  • the design method of the motor control device according to the first embodiment will be described with reference to the flowchart of FIG. More specifically, the design method of the motor control unit 12 will be described.
  • ⁇ indicates the lead angle of the screw in the feed screw mechanism.
  • ⁇ indicates the friction coefficient in the feed screw mechanism (hereinafter referred to as “screw friction coefficient”).
  • Nh Q indicates the frictional force in the feed screw mechanism.
  • Nv Q indicates the drag force in the lead screw mechanism.
  • ⁇ indicates the friction angle in the feed screw mechanism.
  • Q 1 is a force corresponding to the load on the actuator, that is, the operating force by the actuator.
  • T indicates the torque generated by the motor (hereinafter referred to as "motor torque").
  • r indicates the effective radius of the screw in the feed screw mechanism. That is, the effective radius r is a constant.
  • the value of the lead angle ⁇ is determined based on the following equation (5). That is, the lead angle ⁇ is a constant.
  • the value of the friction angle ⁇ is determined based on the following equation (6). That is, the friction angle ⁇ is a value corresponding to the screw friction coefficient ⁇ .
  • P indicates the screw pitch in the feed screw mechanism.
  • D indicates the effective diameter of the screw in the feed screw mechanism. That is, the screw pitch P is a constant.
  • the effective diameter D is a constant. More specifically, the effective diameter D is a value twice the effective radius r.
  • Nh R indicates the frictional force in the feed screw mechanism.
  • Nv R indicates the drag force in the lead screw mechanism.
  • R 1 indicates a force corresponding to the load on the actuator, that is, a holding force by the actuator.
  • the coefficient a is expressed by the following equation (14).
  • the coefficient b is represented by the following equation (15).
  • the coefficient c is represented by the following equation (16).
  • the motor torque T is expressed by the following equation (17) using the friction angle ⁇ . That is, the motor torque T becomes a value corresponding to the screw friction coefficient ⁇ .
  • ⁇ indicates the inclination angle of the thread in the feed screw mechanism. That is, the inclination angle ⁇ is a constant.
  • the actuator 3 is installed in a testing machine (for example, Amsler). Further, the motor 4 is electrically connected to the power supply. The power supply supplies electric power to the motor 4. As a result, torque is generated in a predetermined direction (hereinafter referred to as "torque generation direction").
  • a load in the linear motion direction and a forward load with respect to the torque generation method (hereinafter referred to as "forward load”) is applied to the actuator 3 by the testing machine.
  • a measuring instrument for example, an oscilloscope
  • the load L1 is measured.
  • the value of the current I1 may be referred to as a "first current value”.
  • the value of the voltage V1 may be referred to as a “first voltage value”.
  • the value of the load L1 may be referred to as a "first load value”.
  • a load in the linear motion direction and a load in the opposite direction to the torque generation method (hereinafter referred to as "reverse load”) is applied to the actuator 3 by the testing machine.
  • the measuring instrument measures the current I2 in the motor 4, the voltage V2 in the motor 4, and the load L2 in the linear motion direction in the actuator 3. Be measured.
  • the value of the current I2 may be referred to as a “second current value”.
  • the value of the voltage V2 may be referred to as a “second voltage value”.
  • the value of the load L2 may be referred to as a "second load value”.
  • step ST11 in which the current I1, the voltage V1 and the load L1 in the forward load state are measured may be referred to as a “first measurement step”.
  • step ST12 in which the current I2, the voltage V2, and the load L2 in the reverse load state are measured may be referred to as a “second measurement step”.
  • the first measurement step ST11 and the second measurement step ST12 may be collectively referred to as a “measurement step”.
  • the values (I1, V1, L1, I2, V2, L2) measured in the measurement steps ST11 and ST12 may be referred to as "measured values”.
  • the actuating force Q 1 is calculated. More specifically, the current I1 is equal to the current I2, and, based on the load L1 with respect to the voltage V1 at the time when the current I1 is constant, the actuating force Q 1 is calculated. Or, the voltage V1 is equal to the voltage V2, and, based on the load L1 with respect to the current I1 when the voltage V1 is constant, the actuating force Q 1 is calculated.
  • the holding force R 1 is calculated. More specifically, the current I2 is equal to the current I2, and, based on the load L2 with respect to the voltage V2 of when the current I2 is constant, the holding force R 1 is calculated. Or, the voltage V2 is equivalent to the voltage V1, and, based on the load L2 with respect to the current I2 when the voltage V2 is constant, the holding force R 1 is calculated.
  • the screw friction coefficient ⁇ is calculated by the above equations (13) to (16) using the calculated value of the inverse efficiency Z and the value of the lead angle ⁇ which is a constant.
  • the friction angle ⁇ is calculated by the above equation (6) using the calculated value of the screw friction coefficient ⁇ . Then, the calculated working force to Q 1 value, the value of the effective radius r is a constant, the value of the lead angle ⁇ is a constant, the calculated value of the friction angle theta, and the value of the tilt angle ⁇ is a constant.
  • the motor torque T is calculated by the above equation (17).
  • step ST13 in which the values ( ⁇ , T, ⁇ ) used for generating the model M are calculated may be referred to as a “calculation step”. Further, the value ( ⁇ , T, ⁇ ) calculated in the calculation step ST13 may be referred to as a “calculated value”. These values ( ⁇ , T, ⁇ ) are calculated by a computer or a computer (for example, a personal computer or a workstation).
  • FIG. 5 shows an example of the model M.
  • Various known techniques can be used to generate the model M. Detailed description of these techniques will be omitted.
  • these values ( ⁇ , T, ⁇ ) can be accurately calculated based on the inverse efficiency Z. That is, the error of the value ( ⁇ , T, ⁇ ) in the model M can be made smaller than the value ( ⁇ , T, ⁇ ) in the actual machine of the valve system 6. As a result, a highly accurate model M can be generated.
  • step ST14 in which the model M is generated may be referred to as a “generation step”.
  • the model M is generated by a computer or a computer.
  • the torque thrust conversion formulas F1 and F2 are derived using the model M generated in the generation step ST14.
  • the torque thrust conversion equations F1 and F2 are derived by executing an analysis based on the equation of motion related to the rotational motion of the rotor and the equation of motion related to the linear motion of the shaft.
  • Various known techniques can be used for the analysis using the model M. Detailed description of these techniques will be omitted.
  • step ST15 from which the torque thrust conversion formulas F1 and F2 are derived may be referred to as a “deriving step”.
  • the torque thrust conversion formulas F1 and F2 are derived by a computer or a computer.
  • the motor control unit 12 is designed based on the torque thrust conversion formulas F1 and F2 derived in the derivation step ST15. Specifically, for example, the motor control unit 12 is designed by designing the control circuits C corresponding to the torque thrust conversion formulas F1 and F2.
  • FIG. 6 shows an example of the control circuit C.
  • Various known techniques can be used in the design of the control circuit C. Detailed description of these techniques will be omitted.
  • step ST16 in which the motor control unit 12 is designed may be referred to as a "design step".
  • the motor control unit 12 is designed by a computer or a computer.
  • the torque thrust conversion formulas F1 and F2 can be accurately derived. Therefore, as described in the first embodiment, by using the first torque thrust conversion formula F1, the value of the output torque according to the required operating force can be accurately calculated. Further, by using the second torque thrust conversion formula F2, the torque value according to the required holding force can be accurately calculated. As a result, the control accuracy of the output torque can be improved.
  • the design method according to the second embodiment is the design method of the motor control device 100 for the actuator 3 having the motor 4 and the feed screw mechanism 5, and the forward load with respect to the torque generation direction by the motor 4 is applied.
  • the first measurement step in which the first current value (I1) in the motor 4, the first voltage value (V1) in the motor 4, and the first load value (L1) in the actuator 3 are measured when given to the actuator 3.
  • the second current value (I2) in the motor 4, the second voltage value (V2) in the motor 4, and the second load value in the actuator 3 Reverse efficiency using the measurement values (I1, V1, L1, I2, V2, L2) in the measurement steps ST11 and ST12 including the second measurement step ST12 in which (L2) is measured and the measurement steps ST11 and ST12.
  • a calculation step ST13 in which the value of the screw friction coefficient ⁇ , the value of the motor torque T, and the value of the screw conversion efficiency ⁇ are calculated based on Z is provided.
  • the value of the screw friction coefficient ⁇ , the value of the motor torque T, and the value of the screw conversion efficiency ⁇ can be accurately calculated. That is, the error of the calculated value ( ⁇ , T, ⁇ ) with respect to the value ( ⁇ , T, ⁇ ) in the actual machine of the valve system 6 can be reduced.
  • the design method includes a generation step ST14 in which a model M corresponding to the system including the actuator 3 (valve system 6) is generated by using the calculated values ( ⁇ , T, ⁇ ) in the calculation step ST13.
  • a model M corresponding to the system including the actuator 3 (valve system 6) is generated by using the calculated values ( ⁇ , T, ⁇ ) in the calculation step ST13.
  • the design method includes a derivation step ST15 from which the torque thrust conversion formulas F1 and F2 in the actuator 3 are derived based on the result of the analysis using the model M, and the torque thrust conversion formulas F1 and F2 are pushed by the actuator 3. It includes a first torque thrust conversion type F1 corresponding to a pulling operation and a second torque thrust conversion type F2 corresponding to a position holding operation by the actuator 3.
  • the first torque thrust conversion formula F1 and the second torque thrust conversion formula F2 can be accurately derived.
  • the design method includes a design step ST16 in which the motor control device 100 is designed based on the first torque thrust conversion formula F1 and the second torque thrust conversion formula F2.
  • the designed motor control device 100 more specifically, the motor control unit 12
  • the motor control device of the present invention can be used, for example, in a valve system.

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  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
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  • Control Of Electric Motors In General (AREA)

Abstract

L'invention concerne un dispositif (100) de commande de moteur pour un actionneur (3) comportant un moteur (4) et un mécanisme à vis d'alimentation (5), ledit dispositif (100) de commande de moteur comprenant : une unité de réglage de mode (11) destinée à régler sélectivement le mode de fonctionnement du moteur (4) sur un premier mode de fonctionnement correspondant au fonctionnement de poussée-traction au moyen de l'actionneur (3), ou sur un second mode de fonctionnement correspondant au fonctionnement de maintien de position au moyen de l'actionneur (3) ; et une unité (12) de commande de moteur destinée, lorsque le mode de fonctionnement est réglé sur le premier mode de fonctionnement, à actionner le moteur (4) dans le premier mode de fonctionnement, et lorsque le mode de fonctionnement est réglé sur le second mode de fonctionnement, à actionner le moteur (4) dans le second mode de fonctionnement.
PCT/JP2019/024774 2019-06-21 2019-06-21 Dispositif et procédé de commande de moteur, et procédé de conception associé WO2020255391A1 (fr)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001051239A1 (fr) * 2000-01-12 2001-07-19 Mitsubishi Denki Kabushiki Kaisha Convertisseur de poussee, procede et dispositif de commande de convertisseur de poussee
US20100127646A1 (en) * 2007-04-13 2010-05-27 Cameron International Corporation Actuating Device and Method of Operating an Actuating Device
JP2018059494A (ja) * 2016-09-28 2018-04-12 大豊工業株式会社 電動アクチュエータ及び電動ウェイストゲートバルブシステム

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001051239A1 (fr) * 2000-01-12 2001-07-19 Mitsubishi Denki Kabushiki Kaisha Convertisseur de poussee, procede et dispositif de commande de convertisseur de poussee
US20100127646A1 (en) * 2007-04-13 2010-05-27 Cameron International Corporation Actuating Device and Method of Operating an Actuating Device
JP2018059494A (ja) * 2016-09-28 2018-04-12 大豊工業株式会社 電動アクチュエータ及び電動ウェイストゲートバルブシステム

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