MOTOR CONTROL DEVICE

Abstract

A motor control device controls a motor of a mechanical device. The motor control device includes a command value calculation unit that calculates a command value for controlling the motor, and a disturbance observer unit for estimating a disturbance applied to the mechanical device, based on the command value and rotation information of the motor, and to correct the command value based on the disturbance that is estimated. The disturbance observer unit has parameters that are adjusted to compensate for effects of the disturbance having a specific frequency that is an object of suppression. The parameters are adjusted such that a disturbance, applied to the mechanical device after effects of the disturbance are compensated for, has frequency characteristics corresponding to antiresonance characteristics of the mechanical device.

Description

TECHNICAL FIELD

The present invention relates to a motor control device.

BACKGROUND ART

There conventionally is an electric power steering system. An electric power steering system (hereinafter referred to as “EPS”) assists steering by a steering wheel, by applying torque from a motor to a steering mechanism. A control device of the EPS calculates a target current value according to steering torque applied to the steering wheel, and controls power feed to the motor, based on the target current value that is calculated. Thus, the motor generates torque corresponding to the steering torque.

In EPSs, vibrations generated due to torque ripple of the motor or reduction gear are readily conveyed to the steering wheel. Accordingly, torque differential control, such as described in Patent Document 1, for example, is performed. The control device calculates a torque differential value by differentiation of the steering torque detected by a torque sensor, and corrects the target current value in accordance with the torque differential value that is calculated. This suppresses vibrations due to torque ripple.

RELATED ART DOCUMENTS

Patent Documents

• Patent Document 1: Japanese Unexamined Patent Application Publication No. 2004-224129 (JP 2004-224129 A)

SUMMARY OF THE INVENTION

Problem to be Solved by the Invention

Executing torque differential control certainly does enable suppression of vibrations caused by torque ripple. However, torque differential control may not be able to suppress vibrations due to torque ripple to a required level. Accordingly, there is demand to more appropriately suppress vibrations due to torque ripple. Also, motors are used as drive sources not only for electric power steering systems but also for various types of mechanical devices. There also is demand to reduce vibrations due to torque ripple in the motors of these mechanical devices as well.

Means for Solving the Problem

A motor control device according to an aspect of the present disclosure controls a motor of a mechanical device. The motor control device includes a command value calculation unit configured to calculate a command value for controlling the motor, and a disturbance observer unit configured to estimate a disturbance applied to the mechanical device, based on the command value and rotation information of the motor, and to correct the command value based on the disturbance that is estimated. The disturbance observer unit has a parameter that is adjusted to compensate for effects of the disturbance having a specific frequency that is an object of suppression. The disturbance that is applied to the mechanical device after the effects of the disturbance have been compensated for is a post-compensation disturbance, and the parameter is adjusted such that the disturbance following compensation for the disturbance has a frequency characteristic corresponding to an antiresonance characteristic of the mechanical device.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a configuration diagram of an embodiment of a motor control device.

FIG. 2 is a block diagram of the motor control device in FIG. 1.

FIG. 3 is a graph showing frequency characteristics of disturbance.

MODES FOR CARRYING OUT THE INVENTION

A motor control device 11 according to an embodiment will be described.

As illustrated in FIG. 1, the motor control device 11 controls a motor 12. The motor 12 generates torque for driving a mechanical device 13 in which the motor 12 is to be installed. The motor 12 is, for example, a three-phase brushless motor. The motor 12 has a rotation angle sensor 12A. The rotation angle sensor 12A detects a rotation angle θ of the motor 12. The rotation angle θ of the motor 12 is rotation information of the motor 12.

The motor control device 11 has a microcomputer 21, an inverter 22, and a current sensor 23.

The microcomputer 21, which is a processing circuit, has a command value calculation unit 31 and a feedback calculation unit 32. These calculation units are functional parts realized by a CPU (central processing unit) of the microcomputer 21 executing a control program. The microcomputer 21 includes memory that stores the control program. The memory includes computer-readable media such as RAM (Random Access Memory) and ROM (Read Only Memory). However, each calculation unit being realized by software is only an example, and at least part of the calculation units may be realized by a hardware circuit such as a logic circuit.

The command value calculation unit 31 calculates a current command value I* for the motor 12 based on a state variable S_SV indicating a state of the mechanical device 13, for example. The feedback calculation unit 32 calculates a difference between the current command value I* calculated by the command value calculation unit 31 and a value of a current Im of the motor 12 detected by way of the current sensor 23. The feedback calculation unit 32 generates a drive signal for the inverter 22 so as to eliminate the difference between the current command value I* and the value of the current Im of the motor 12.

The inverter 22 operates based on the drive signal generated by the feedback calculation unit 32. The inverter 22 has a plurality of switching elements. By switching these switching elements based on the drive signal, electric power according to the current command value I* is generated. The electric power generated by the inverter 22 is supplied to the motor 12 via a power supply path made up of a bus bar, a cable, or the like. Thus, the motor 12 generates torque corresponding to the current command value I*.

<Disturbance Observer>

As illustrated in the block diagram of FIG. 2, the motor control device 11 has a disturbance observer unit 33. The disturbance observer unit 33 is provided to estimate a disturbance T_ld that is applied to a plant P, which is an object of control, and to compensate for effects of the disturbance T_ld. Compensation for the effects of disturbance refers to reducing the effects of disturbance by taking into account characteristics of the disturbance when controlling a system that is subject to disturbance. The disturbance T_ld is nonlinear torque. The disturbance T_ld is, for example, a torque ripple of the motor 12. Torque ripple is a disturbance that occurs periodically as the motor 12 rotates.

A control system for the motor 12 is a feedback control system that determines the current command value I* for the motor 12 based on the state variable S_SV of the mechanical device 13. Supplying current from the inverter 22 to the motor 12 in accordance with the current command value I* rotates the motor 12 at a predetermined angular velocity ω_m. Therefore, a range from the current command value I* for the motor 12, to the angular velocity ω_m of the motor 12, is the object of control target in the feedback control system. The angular velocity ω_m of the motor 12 is rotation information of the motor 12. The plant P includes the mechanical device 13.

When the inertial number of the mechanical device 13 is “1”, and the mechanical device 13 and the motor 12 are regarded as being connected via an elastic element, the object of control can be regarded as being a two-inertial system in which two moments of inertia are connected by the elastic element. In this case, the object of control has frequency characteristics that include one set of resonance characteristics and antiresonance characteristics.

Also, when the inertial number of the mechanical device 13 is “2”, and the mechanical device 13 and the motor 12 are regarded as being connected via an elastic element, the object of control can be regarded as being a three-inertial system in which three moments of inertia are connected by the elastic element. In this case, the object of control has frequency characteristics that include two sets of resonance characteristics and antiresonance characteristics.

The disturbance observer unit 33 takes in the current command value I*, which is a target value of the plant P, and output of the plant P. An example of the output of the plant P is the angular velocity ω_m of the motor 12. The angular velocity Ω_m is obtained by differentiation of the rotation angle θ of the motor 12 that is detected by the rotation angle sensor 12A. The disturbance observer unit 33 estimates the disturbance T_ld based on the current command value I* and the angular velocity ω_m of the motor 12. The disturbance observer unit 33 calculates a first correction value I_c1 for canceling out the disturbance T_ld having a frequency that is the object of suppression.

The disturbance observer unit 33 has an estimator 33A, a multiplier 33B, and a subtractor 33C. The disturbance observer unit 33 may be made up of a hardware circuit, such as a logic circuit. The disturbance observer unit 33 is also referred to as a disturbance observer circuit. Also, the disturbance observer unit 33 may be a functional part realized by a CPU of a computer executing a control program.

The estimator 33A has a nominal plant Pn, a first observer gain L1, and a second observer gain L2. The nominal plant Pn is a model simulating the plant P that is the object of control. The estimator 33A calculates a difference Δω between the angular velocity ω_m of the motor 12 obtained as the output of the plant P, and an estimated angular velocity ω_m{circumflex over ( )} of the motor 12 obtained as output of the nominal plant Pn, as shown in the following Expression (1). The “{circumflex over ( )}” indicates an estimated value.

$\begin{array}{cc}\mathrm{\Delta \omega }={\omega }_m-{\omega }_m^& \left(1\right)\end{array}$

The estimator 33A multiplies the value of the difference Δω between the angular velocity Ω_m of the motor 12 and the estimated angular velocity ω_m{circumflex over ( )} of the motor 12 by the second observer gain L2, as shown in the following Expression (2), thereby calculating a differential value dT_ld{circumflex over ( )} of an estimated disturbance T_ld{circumflex over ( )}.

$\begin{array}{cc}{\mathrm{dT}}_{\mathrm{ld}}^=\mathrm{\Delta \omega }·L2& \left(2\right)\end{array}$

Note that the estimator 33A calculates the estimated disturbance T_ld{circumflex over ( )} by integration of the differential value dT_ld{circumflex over ( )} of the estimated disturbance T_ld{circumflex over ( )}. The nominal plant Pn calculates an estimated value ω_m{circumflex over ( )} of the angular velocity ω_m using the estimated disturbance T_ld{circumflex over ( )}, a value obtained by multiplying the value of the difference Δω by the first observer gain L1, and a viscosity coefficient C of the motor 12.

The multiplier 33B calculates the first correction value I_c1 by multiplying the differential value dT_ld{circumflex over ( )} of the estimated disturbance T_ld{circumflex over ( )} calculated by the estimator 33A, by a gain β. The first correction value I_c1 is a current value for canceling out the vibration due to the disturbance T_ld.

The subtractor 33C subtracts the first correction value I_c1 from the current command value I* to calculate a current command value I* in which the effects of the disturbance T_ld have been compensated for.

The disturbance T_ld that is applied to the mechanical device 13 after the effects of the disturbance T_ld have been compensated for by the disturbance observer unit 33 is referred to as post-compensation disturbance T_last.

The post-compensation disturbance T_last is expressed by the following Expression (3).

$\begin{array}{cc}{T}_{last}=T_{ld}-\beta ·{\mathrm{dT}}_{\mathrm{ld}}^=\{{\mathrm{Js}}^2+\left(-L2·\beta \right)+L1·J)s+L2\}·T_{ld}/\left\{{\mathrm{Js}}^2+\left(-L2·C+L1·J\right)s+L2\right\}·\mathrm{Js}& \left(3\right)\end{array}$

where “J” is a coefficient of inertia in which a moment of inertia of the mechanical device 13 is modeled, “C” is a viscosity coefficient in which friction of the mechanical device 13 is modeled, “s” is a Laplace operator, “L1” is first observer gain, “L2” is second observer gain, and “β” is gain.

As shown in the graph of FIG. 3, the post-compensation disturbance T_last has a notch, which is a spike-like drop, in frequency characteristics thereof. The post-compensation disturbance T_last has frequency characteristics corresponding to the antiresonance characteristics of the plant P.

The first observer gain L1 is expressed by the following Expression (4).

$\begin{array}{cc}L1=2·\omega ·\alpha & \left(4\right)\end{array}$

where “Ω” is frequency, and “α” is a first parameter.

The second observer gain L2 is expressed by the following Expression (5).

$\begin{array}{cc}L2=J·{\omega }^2& \left(5\right)\end{array}$

where “J” is a coefficient of inertia in which the moment of inertia of the mechanical device 13 is modeled, and “Ω” is frequency.

The gain β is expressed by the following Expression (6).

$\begin{array}{cc}\beta =\alpha /\omega ·2·\gamma & \left(6\right)\end{array}$

where “α” is a first parameter, “Ω” is frequency, and “γ” is a second parameter. The second parameter γ is a value of “1” or less, and can be set, for example, in steps of “0.1”.

The value of the frequency Ω is set to the frequency of the disturbance T_ld to be suppressed, and the frequency of the disturbance T_ld to be suppressed is, for example, the center frequency fc of the notch in the disturbance T_ld.

Further, adjusting the value of the first observer gain L1 enables a width W_n of the notch in the disturbance T_ld to be adjusted. Adjusting the value of the first parameter α in Expression (4) enables the value of the first observer gain L1 to be adjusted.

Also, adjusting the value of the gain β enables a depth D_n of the notch in the disturbance T_ld to be adjusted. Adjusting the value of the second parameter γ in Expression (6) enables the value of the gain β to be adjusted.

The first observer gain L1 and the gain β are parameters that are adjusted to suppress vibrations due to the disturbance T_ld having a specific frequency that is the object of suppression. Adjusting the value of the first observer gain L1 and the value of the gain β enables a conveyance rate of the disturbance T_ld to the plant P to be adjusted. The value of the first observer gain L1 and the value of the gain β are adjusted so that the post-compensation disturbance T_last has frequency characteristics corresponding to the antiresonance characteristics of the plant P. Inputting the post-compensation disturbance T_last having frequency characteristics corresponding to the antiresonance characteristics of the plant P into the plant P theoretically enables the amplitude of vibrations of the mechanical device 13 due to the disturbance T_ld having a specific frequency that is the object of suppression to be set to “0”.

Substituting Expressions (4), (5), and (6) into the above Expression (3) yields the following Expression (7).

$\begin{array}{cc}{T}_{last}=\left\{s^2+2·\omega ·\alpha ·\left(1-\gamma \right)·s+{\omega }^2\right\}·T_{ld}/\left\{s^2+2·\omega ·\alpha ·s+{\omega }^2\right\}& \left(7\right)\end{array}$

When the value of the second term “2·Ω·α·(1−γ)·s” in the curly brackets in the numerator of Expression (7) is “0”, the conveyance rate of the disturbance T_ld having the specific frequency that is the object of suppression with respect to the plant P becomes “0”. Accordingly, setting the value of the second parameter γ to “1” enables the vibrations due to the disturbance T_ld having the specific frequency that is the object of suppression to be cancelled out. Furthermore, adjusting the value of the second parameter γ between “0 and 1” in steps of “0.1”, for example, enables the conveyance rate of the disturbance T_ld having the specific frequency that is the object of suppression with respect to the plant P to be adjusted. The smaller the value of the second term “2·Ω·α·(1−γ)·s” in the curly brackets in the numerator of Expression (7) becomes, the smaller the conveyance rate of the disturbance T_ld having the specific frequency that is the object of suppression with respect to the plant P becomes.

Note that the second term in the curly brackets in the numerator of Expression (7), “2·Ω·α·(1−γ)·s”, corresponds to the second term in the curly brackets in the numerator of Expression (3), “(−L2·β)+L1·J)s”. To adjust the value of the second parameter γ is also to adjust the value of the gain β.

Effects of Embodiment

According to the present embodiment, the following effects can be obtained.

(1) The disturbance observer unit 33 estimates the disturbance T_ld using a nominal plant Pn that is a model simulating the plant P, and corrects the current command value I* based on the disturbance T_ld that is estimated. The disturbance observer unit 33 has parameters that are adjusted to suppress vibrations due to the disturbance T_ld having the specific frequency that is the object of suppression. Adjusting these parameters enables compensating just for the effects of the disturbance T_ld having the specific frequency that is the object of suppression. The parameters are adjusted so that the post-compensation disturbance T_last has frequency characteristics corresponding to the antiresonance characteristics of the plant P. Inputting the post-compensation disturbance T_last having frequency characteristics corresponding to the antiresonance characteristics of the plant P to the plant P enables vibrations occurring in the plant P to be suppressed or canceled out.

(2) The disturbance observer unit 33 estimates the disturbance T_ld applied to the mechanical device 13 based on the current command value I* and the angular velocity ω_m of the motor 12. Unlike in the case in which the rotation angle θ of the motor 12 is used, there is no need to calculate the midpoint of the motor 12. The midpoint of the motor 12 is the rotation angle θ of the motor 12 corresponding to the reference operating state of the mechanical device 13. Accordingly, the motor control device 11 does not need to have a function of calculating the midpoint of the motor 12.

(2) The disturbance observer unit 33 calculates the first correction value I_c1 for the current command value I* by multiplying the differential value dT_ld{circumflex over ( )} of the estimated disturbance T_ld{circumflex over ( )} by the gain β. Multiplying the differential value dT_ld{circumflex over ( )} by the gain β is all that is necessary, and accordingly the first correction value I_c1 can be easily calculated.

(3) The post-compensation disturbance T_last that is applied to the plant P after the effects of the disturbance T_ld have been compensated for has conveyance characteristics expressed by the following Expression (A). This is based on Expression (3) above.

$\begin{array}{cc}\{{\mathrm{Js}}^2+\left(-L2·\beta \right)+L1·J)s+L2\}/\left\{{\mathrm{Js}}^2+\left(-L2·C+L1·J\right)s+L2\right\}·\mathrm{Js}& \left(A\right)\end{array}$

When the value of the second term “(−L2·B)+L1·J)s” in the numerator of Expression (A) is “0”, the conveyance rate of the disturbance T_ld to the plant P theoretically becomes “0”. Accordingly, the value of the gain β of the disturbance observer unit 33 is adjusted so that the value of the second term of the numerator of Expression (A) becomes “0” or a value closer to “0”. Adjusting the value of the gain β enables the disturbance T_ld to be suppressed more appropriately.

OTHER EMBODIMENTS

The present embodiment may be carried out modified as follows.

• • As indicated by the long dashed double-short dashed lines in FIG. 2, the disturbance observer unit 33 may have a disturbance feedback controller 33D and an adder 33E. The disturbance feedback controller 33D takes in the differential value dT_ld{circumflex over ( )} of the estimated disturbance T_ld{circumflex over ( )} calculated by the estimator 33A, and calculates a second correction value I_c2 based on the differential value dT_ld{circumflex over ( )} of the estimated disturbance T_ld{circumflex over ( )} that is taken in. The second correction value I_c2 is a current value corresponding to the estimated disturbance T_ld{circumflex over ( )} which is the difference between the actual motor output and the estimated motor output. The adder 33E calculates the final current command value I* by adding the second correction value I_c2 to the current command value I* obtained after the effects of the disturbance id are compensated for. The feedback calculation unit 32 performs feedback control of the current supplied to the motor 12 based on the final current command value I*. Thus, the value of the current supplied to the motor 12 tracks the current command value I* more quickly.
  • The mechanical device 13 may be an electric power steering system. The motor 12 is an assisting motor. The assisting motor generates assisting torque that is applied to the steering mechanism of the vehicle. The assisting torque is a torque for assisting steering by the steering wheel. The steering mechanism includes a steering shaft connected to steering wheels, and a turning shaft that steers the steered wheels of the vehicle. The assisting torque is applied to the steering shaft or the turning shaft. The command value calculation unit 31 calculates the current command value I* for the assisting motor, in accordance with steering torque T_h detected by the torque sensor. The steering torque T_h is the torque applied to the steering wheel. The steering torque T_h is a state variable S_SV indicating the steering state of the steering system.
  • The mechanical device 13 may be a steer-by-wire steering system. The motor 12 is a reaction force motor or a steering motor. The reaction force motor generates a steering reaction torque that is applied to the steering shaft of the vehicle. The steering reaction torque is a torque in an opposite direction of a steering direction of the steering wheel. The command value calculation unit 31 calculates the current command value I* for the reaction force motor, in accordance with steering torque T_h detected by the torque sensor. The steering motor generates steering torque for steering the steered wheels of the vehicle. The command value calculation unit 31 calculates the current command value I* for the steering motor in accordance with the steering angle of the steering wheel. The steering angle is calculated, for example, based on the rotation angle θ of the motor 12 detected by the rotation angle sensor 12A. The steering torque T_h and the steering angle are the state variable S_SV indicating the steering state of the steering system.
  • As indicated by the long dashed double-short dashed lines in FIG. 2, when the motor 12 is an assisting motor or a reaction force motor, the motor control device 11 may be configured as follows. That is to say, the motor control device 11 has a compensator 34 and a multiplier 35. The compensator 34 calculates a torque differential value by differentiation of the steering torque T_h detected by the torque sensor, and calculates a compensation amount dT_ca for compensating for the effects of the disturbance T_ld in accordance with the torque differential value that is calculated. The multiplier 35 calculates a third correction value I_c3 by multiplying the compensation amount dT_ca by the gain β. The third correction value I_c3 is a current value. The subtractor 33C adds the third correction value I_c3 to the current command value I*. This increases responsiveness of the motor torque as to changes in the steering torque T_h. Thus, a smoother steering feel can be obtained. Also, advantages of suppressing disturbances, such as reverse input vibration from the steered wheels, brake vibrations generated due to brake operations, and so forth, can also be obtained.
  • When the mechanical device 13 is a steering system of a vehicle, and the motor 12 is an assisting motor or a reaction force motor, the disturbance observer unit 33 may be configured as follows. That is to say, the disturbance observer unit 33 may stop disturbance compensation control, which is control for compensating for the effects of the disturbance T_ld, in a state in which vibrations due to torque ripple of the motor 12 are unlikely to appear in the steering system. For example, vibrations due to torque ripple are easily conveyed to the steering system when the vehicle speed is an extremely low speed. Accordingly, the disturbance observer unit 33 may stop the disturbance compensation control when a value of the vehicle speed exceeds a vehicle speed threshold. The speed threshold is a standard for determining whether the vehicle speed is an extremely low speed. Also, vibrations due to torque ripple are easily conveyed to the steering system when the angular velocity ω_m of the motor 12 is extremely slow. Accordingly, the disturbance observer unit 33 may stop the disturbance compensation control when a value of the angular velocity Ω_m exceeds an angular velocity threshold. The angular velocity threshold is a standard for when determining whether the angular velocity ω_m of the motor 12 is extremely slow. The angular velocity ω_m of the motor 12 reflects the steering speed of the steering wheel.
  • The motor control device 11 may have a function of detecting an abnormality in itself, an abnormality in the motor 12, or an abnormality in the mechanical device 13. In this case, the disturbance observer unit 33 may stop the disturbance compensation control when an abnormality in the motor control device 11, the motor 12, or the mechanical device 13, is detected. Executing compensation control when an abnormality is detected in the motor control device 11, the motor 12, or the mechanical device 13, is meaningless.
  • The command value calculation unit 31 may be configured as follows. That is to say, an arrangement may be made in which the command value calculation unit 31 calculates a torque command value based on the state variable S_SV indicating the state of the mechanical device 13, and calculates the current command value I* based on this torque command value that is calculated. The torque command value is the torque that the motor 12 is to be caused to generate. In this case, the estimator 33A takes in the torque command value and the angular velocity ω_m of the motor 12, which is the output of the plant P. The estimator 33A calculates the differential value dT_ld{circumflex over ( )} of the estimated disturbance T_ld{circumflex over ( )} based on the torque command value and the angular velocity ω_m of the motor 12. The multiplier 33B calculates a torque correction value by multiplying the differential value dT_ld{circumflex over ( )} of the estimated disturbance T_ld{circumflex over ( )} by a predetermined gain. The torque correction value is a correction value for the torque command value. The subtractor 33C corrects the torque command value by subtracting the torque correction value from the torque command value. In this arrangement as well, the effects of the disturbance T_ld having the frequency that is the object of suppression can be compensated for.
  • The disturbance observer unit 33 may be configured as follows. That is to say, the disturbance observer unit 33 may calculate the difference between the rotation angle θ of the motor 12 obtained as the output of the plant P and the estimated rotation angle of the motor 12 obtained as the output of the nominal plant Pn, and compensate for the effects of the disturbance T_ld based on the difference value that is calculated in this way. The rotation angle θ of the motor 12 is rotation information of the motor 12.
  • The mechanical device 13 is not limited to being a vehicle steering system. The mechanical device 13 may be a machine tool driven by a motor, for example.

Claims

1. A motor control device that controls a motor of a mechanical device, the motor control device comprising: a command value calculation unit configured to calculate a command value for controlling the motor; anda disturbance observer unit configured to estimate a disturbance applied to the mechanical device, based on the command value and rotation information of the motor, and to correct the command value based on the disturbance that is estimated, whereinthe disturbance observer unit has a parameter that is adjusted to compensate for effects of the disturbance having a specific frequency that is an object of suppression,the disturbance that is applied to the mechanical device, after the effects of the disturbance have been compensated for, is a post-compensation disturbance, andthe parameter is adjusted such that the post-compensation disturbance has a frequency characteristic corresponding to an antiresonance characteristic that appears in control of the motor in the mechanical device.

2. The motor control device according to claim 1, wherein the rotation information of the motor is an angular velocity of the motor.

3. The motor control device according to claim 2, wherein the disturbance observer unit is configured to calculate a differential value of the disturbance based on the command value and the angular velocity of the motor, andcalculate a first correction value for the command value by multiplying, by a gain, the differential value of the disturbance that is calculated.

4. The motor control device according to claim 3, wherein with “J” as a coefficient of inertia of the mechanical device, “C” as a viscosity coefficient of the mechanical device, “s” as a Laplace operator, “L1” as a first observer gain of the disturbance observer unit, “L2” as a second observer gain of the disturbance observer unit, and “β” as the gain, the post-compensation disturbance has conveyance characteristics expressed by the following Expression (A) {Js2+(−L2·β)+L1·J)s+L2}/{Js2+(−L2·C+L1·J)s+L2}·Js . . . (A), and a value of “β” that is the gain is adjusted such that a value of a second term of a numerator of Expression (A) becomes zero or a value closer to zero.

5. The motor control device according to claim 2, wherein the disturbance observer unit is configured to calculate a differential value of the disturbance based on the command value and the angular velocity of the motor, andcalculate a second correction value for the command value based on the differential value of the disturbance that is calculated.

6. The motor control device according to claim 1, wherein: the mechanical device is configured to also operate due to torque being applied externally; andthe disturbance observer unit is configured to calculate a compensation amount for compensating for the effects of the disturbance in accordance with a differential value of the torque externally applied to the mechanical device, andcalculate a third correction value for the command value based on the compensation amount that is calculated.

7. The motor control device according to claim 1, wherein: the mechanical device is a steering system of a vehicle; andthe motor generates a torque that is applied to the steering system.