JP2007314094A - Electric pump device and power steering device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an electric pump drive device avoiding deterioration of steering feeling even if fluctuation of number of rotations of a pump is generated. <P>SOLUTION: The electric pump device has the pump for feeding a liquid pressure; an electric motor for driving the pump; an electric motor control circuit for outputting a drive instruction signal to the electric motor; a rotation speed measurement means for detecting or measuring a rotation speed of the electric motor; and a drive signal correction means for correcting the drive instruction signal so as to deny predetermined high frequency component fluctuation of a rotation speed component measured by the rotation speed measurement means. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an electric pump device, and more particularly to an electric pump device applied to a power steering device that assists a driver's steering.

  Conventionally, in the power steering apparatus disclosed in Patent Document 1, steering assist is provided by selectively supplying hydraulic pressure from a reversible pump driven by an electric motor to the left and right cylinder chambers of the power cylinder. Gaining power.

This electric motor is driven only at the time of steering, and is stopped at the time of non-steering such as when traveling straight ahead, thereby reducing power consumption. Furthermore, by appropriately controlling the driving speed of the electric motor according to the steering speed and the steering torque, an appropriate pump discharge pressure corresponding to the steering situation is obtained. Therefore, the electric motor, that is, the reversible pump has a characteristic that the rotational speed control region is large.
JP-A-2005-41301

  However, in the above prior art, when the hydraulic pump is driven by an electric motor, unintentional fluctuations in the pump rotation speed may occur depending on the load state of the hydraulic pump and the friction state of the electric motor. This rotational fluctuation becomes a hydraulic pressure change, resulting in a fluctuation of the steering assist force, resulting in a problem that the steering feeling is deteriorated.

  The present invention has been made paying attention to the above-described problems, and an object of the present invention is to provide an electric pump drive device that avoids deterioration of steering feeling even if fluctuations in pump rotation speed occur. .

  In order to achieve the above object, in the present invention, a pump that supplies hydraulic pressure, an electric motor that drives the pump, an electric motor control circuit that outputs a drive command signal to the electric motor, and a rotational speed of the electric motor A rotational speed measuring means for detecting or measuring the drive speed, and a drive signal correcting means for correcting the drive command signal so as to cancel a predetermined high-frequency component fluctuation among the rotational speed components measured by the rotational speed measuring means. It was.

  Therefore, it is possible to provide an electric pump drive device that avoids deterioration of the steering feeling even if the pump rotational speed fluctuates.

  Hereinafter, a pump device and a power steering device to which an electric pump device of the present invention is applied will be described based on embodiments shown in the drawings.

  FIG. 1 is a system diagram showing an overall configuration of a power steering apparatus according to Embodiment 1 of the present invention. 1 is a steering wheel, 2 is a steering shaft, 3 is a rack and pinion mechanism (steering mechanism), 5 is a power steering mechanism that assists the steering force of the driver, 6 is an external gear type bidirectional pump driven by a motor M, 7 is a steering wheel, 8 is a warning lamp for notifying the driver that a failure has occurred in the steering system, and 10 is a control unit (motor control circuit).

  The motor M is a brushless motor and is provided with a motor rotation speed sensor M / Sen (rotational speed measuring means) including three Hall elements that detect the rotation angle of the electric motor.

  The bidirectional pump P that is a hydraulic source of the power steering mechanism 5 is provided on a hydraulic pipe 61 that communicates the first cylinder chamber 51 and the second cylinder chamber 52 of the power cylinder 5a (hydraulic power cylinder). When the driver operates the steering wheel 1, the rotation direction of the motor M is switched according to the operation direction, and the driver's steering is performed by supplying and discharging oil between the first cylinder chamber 51 and the second cylinder chamber 52. Assist force.

  Specifically, when the steering wheel 1 is steered to the right in the drawing, the motor M is driven in the direction in which the hydraulic pressure is supplied from the second cylinder chamber 52 to the first cylinder chamber 51 to move integrally with the rack shaft 54. The piston 53 is assisted to the second cylinder chamber 52 side.

  The hydraulic pipe 61 is provided with a bypass circuit 62 that communicates the first cylinder chamber 51 and the second cylinder chamber 52 without passing through the bidirectional pump P. On the bypass circuit 62, an electronically controlled fail-safe valve 4 that operates based on a command signal from the control unit 10 is provided.

  The fail-safe valve 4 uses a normally open valve that is closed when a voltage is supplied in response to a command signal from the control unit 10 and is open when no voltage is supplied.

  As a result, even if some abnormality occurs in the steering system and the power supply is shut down, the first cylinder chamber 51 and the second cylinder chamber 52 can be in communication with each other. Ensure steering.

  Further, the steering shaft 2 is provided with a torque sensor 12 for detecting the steering torque of the driver.

  The control unit 10 includes a steering torque signal from the torque sensor 12, an IGN signal from the ignition switch 13, an engine speed signal from the engine speed sensor 14, a vehicle speed signal from the vehicle speed sensor 15, and a motor speed sensor M / Sen. The motor rotation signal from is input. Based on these input signals, command signals are output to the motor M, the fail safe valve 4 and the warning lamp 8 of the bidirectional pump P.

  FIG. 2 is a block diagram showing the configuration inside the control unit 10. The power supply circuit watchdog timer 101 receives a voltage signal from the power supply 11 and an IGN signal from the ignition switch 13 and transmits / receives a signal to / from the main microcomputer 107.

  The engine speed processing circuit 102 outputs an engine speed signal from the engine speed sensor 14 to the main microcomputer 107. The torque sensor processing circuit 103 outputs a torque signal from the torque sensor 12 to the main microcomputer 107 and also outputs it to the sub-microcomputer 108.

  The vehicle speed signal processing circuit 104 outputs a vehicle speed signal from the vehicle speed sensor 15 to the main microcomputer 107. The diagnostic circuit 105 outputs a diagnostic signal input via the connector 16 to the main microcomputer. The CAN communication circuit 106 outputs a signal transmitted by the vehicle system CAN to the main microcomputer 107.

  The sub microcomputer 108 monitors the main microcomputer 107. When a failure occurs in the main microcomputer 107, a control signal can be output to the fail safe relay 109, the fail safe valve driving circuit 116, and the warning lamp driving circuit 117.

  The fail safe relay 109 cuts off the power supply for driving the electric motor when any failure occurs. The EEPROM 110 stores various data necessary for control and can update the data.

  The fail safe relay diagnosis input circuit 111 outputs an operation diagnosis signal for the fail safe relay 109 to the main microcomputer 107.

  The electric motor drive circuit 112 supplies a voltage to the motor M based on a command signal from the main microcomputer 107. The current monitor circuit 113 detects the current value of the motor M and outputs it to the main microcomputer 107. The motor terminal voltage circuit 114 outputs the terminal voltage of the motor M to the main microcomputer 107.

  The motor rotation signal processing circuit 115 calculates the rotation speed ω from the three Hall elements provided in the motor M, and outputs the rotation speed ω to the main microcomputer 107.

  By calculating the motor speed ω using the output of the motor speed sensor M / Sen provided in the brushless motor, there is no need to provide a separate sensor. Further, since the motor rotation speed sensor M / Sen detects the rotation position of the rotation shaft of the brushless motor, it obtains a highly accurate rotation speed signal of the motor.

  The fail safe valve drive circuit 116 outputs a drive signal to the fail safe valve 4 based on a command signal from the main microcomputer 107 or the sub microcomputer 108. The warning lamp drive circuit 117 outputs a command signal to the warning lamp 8 based on a command signal from the main microcomputer 107 or the sub-microcomputer 108.

  FIG. 3 is a schematic diagram illustrating the configuration of the pump unit according to the first embodiment. First, the configuration will be described. The hydraulic pipes 61a, 61b, 61c, 61d connect the cylinder chambers 51 to the bidirectional pump P. The bypass oil passages 62a, 62a ′, 62b, 62b ′ communicate with the hydraulic pipes 61b, 61c.

  The reservoir tanks 202a, 202b, and 205 supply oil to the bidirectional pump P and store drained oil. For convenience of explanation, it is shown that there are a plurality of reservoir tanks, but one reservoir tank may be provided. The check valves 201a and 201b are closed when hydraulic pressure is generated by the bidirectional pump P, and are opened when negative pressure is generated.

  Details of the return check valve 203 will be described later. A check valve 204 (corresponding to a check valve described in claims) supplies drained oil to the reservoir tank 205. The drain oil passage 63 is connected via a return check valve 203, a reservoir tank 205, and a check valve 204.

  Here, the return check valve 203 will be described. The return check valve 203 includes a first return check valve 203a, a second return check valve 204a), a spool valve 210, and return springs 206a and 206b that urge the spool valve 210 to the center.

  The first return check valve 203a is provided with a first hydraulic chamber 207a having a connection port for the hydraulic pipes 61a and 61b, and a first piston chamber 208a having a connection port for the drain oil passage 63 and the bypass oil passage 62a ′. It has been. Similarly, the second return check valve 203b includes a second hydraulic chamber 207b having a connection port with the hydraulic pipes 61c and 61d, and a second piston chamber 208b having a connection port with the drain oil passage 63 and the bypass oil passage 62b ′. Is provided.

  The spool valve 210 is acted on by the urging force on the right side in the figure by the urging force of the return spring 206a, the oil pressure of the first hydraulic chamber 207a, and the oil pressure of the first piston chamber 208a. On the other hand, as the biasing force on the opposite side (left side in the figure), the biasing force by the return spring 207a, the hydraulic pressure in the second hydraulic chamber 207b, and the hydraulic pressure in the second piston chamber 208b act. Thereby, the position of the spool valve 210 is determined.

  The spool valve 210 is acted on by the urging force on the right side in the figure by the urging force of the return spring 206a, the oil pressure of the first hydraulic chamber 207a, and the oil pressure of the first piston chamber 208a. On the other hand, as the biasing force on the opposite side (left side in the figure), the biasing force by the return spring 207a, the hydraulic pressure in the second hydraulic chamber 207b, and the hydraulic pressure in the second piston chamber 208b act. Thereby, the position of the spool valve 210 is determined.

  FIG. 4 is a diagram illustrating the flow of oil during normal torque assist control, and FIG. 5 is an operation explanatory diagram illustrating the movement of the return check valve. In FIG. 4, a thick solid line indicates a high hydraulic pressure, and a thick dotted line indicates a low hydraulic pressure.

(When steering from the neutral position)
A description will be given of steering from a position where the hydraulic pressure in the first cylinder chamber 51 and the hydraulic pressure in the second cylinder chamber 52 are balanced. At the start of steering, the hydraulic pressure in the first cylinder chamber 51 and the hydraulic pressure in the second cylinder chamber 52 are in a balanced state. When assisting the rack shaft 54 to the right side in the figure by the driver's steering, the bidirectional pump P is driven to supply hydraulic pressure to the second cylinder chamber 52. Then, the hydraulic pipe 61c and the hydraulic pipe 61d become high hydraulic pressure.

  This high oil pressure is also supplied to the bypass oil passages 62b and 62d ', and the second piston chamber 208b becomes a high oil pressure. At this time, since the fail safe valve 4 is closed, as shown in FIG. 5B, the first piston chamber 208a and the second piston chamber 208b, and the first hydraulic chamber 207a and the second hydraulic chamber 207b are different. Pressure is generated and the spool valve 210 is moved to the left in FIG.

  Thereby, the bypass oil passage 62a ′ and the drain oil passage 63 are communicated with each other, and the first cylinder chamber 51 has a low hydraulic pressure released to the atmosphere. Torque assist steering is executed using this differential pressure.

[Control configuration of motor drive]
FIG. 6 is a control block diagram of a portion used for motor driving in the control unit 10. The main microcomputer 107 includes a target torque calculation unit 70, a torque-current conversion unit 71, a PI control unit 72, a two-phase / three-phase conversion unit 73, a three-phase / two-phase conversion unit 74, and a correction unit 75.

  The target torque calculator 70 calculates a target torque T * of the motor M based on the steering torque signal and outputs it to the torque-current converter 71.

  Based on the rotational speed ω of the motor M, the torque-current converter 71 converts the target torque T * into d and q-axis current target values di * and qi * of the motor M, and converts the d-axis current target value di * into PI. The control unit 72 outputs the q-axis current target value qi * to the correction unit 75.

  The correction unit 75 corrects the q-axis current target value qi * based on the motor rotational speed ω, reduces the rotational fluctuation of the motor M due to disturbance, and outputs it to the PI control unit 72.

  The PI control unit 72 performs PI control on the input d and q-axis current target values di * and qi * to calculate d and q-axis command currents dis and qis, and outputs them to the two-phase to three-phase conversion unit 73. To do.

  The two-phase / three-phase converter 73 converts the d and q-axis command currents dis and qis into U, V, and W three-phase command voltages and outputs them to the motor drive circuit 112.

  The three-phase to two-phase conversion unit 74 converts the detected current values of the U, V, and W phases detected by the current monitor circuit 113 into two phases corresponding to the d and q axes, and outputs them.

  The motor drive circuit 112 performs PWM conversion on the U, V, and W phase command voltages in the PWM output control unit 112a, and outputs the converted voltage to the motor M via the inverter circuit 112b.

[Control configuration of correction unit]
FIG. 7 is a control block diagram of the correction unit 75, and FIG. 8 is a diagram illustrating the relationship between the input frequency f and the output gain K _HPF in the high-pass filter HPF provided in the correction unit 75.

The correction unit 75 processes the motor rotational speed ω by the high-pass filter HPF, multiplies the processed ω · K _HPF by the current conversion coefficient K and subtracts it from the q-axis current target value qi *, and then corrects the corrected q-axis current target value qi *. Output as.

  At the time of output, in order to prevent the torque of the motor M from changing suddenly, the corrected q-axis current target value qi * is gradually decreased or increased. Further, by suppressing the correction amount within a predetermined range, it is possible to avoid the q-axis current target value qi * from fluctuating more than necessary before and after the correction.

  The high-pass filter HPF is a filter circuit that extracts a high-frequency component of the output signal from the motor rotation speed sensor M / Sen. By extracting only the high frequency components, only the desired high frequency components are corrected.

That is, the high-pass filter HPF reads the output gain K _HPF from the motor rotation frequency f = 1 / ω and cuts off the frequency f equal to or lower than the predetermined value fa. A frequency equal to or higher than a predetermined value fa that has passed through the high-pass filter HPF is multiplied by a current conversion coefficient K and subtracted from the q-axis target current qi * before correction.

  Accordingly, the vibration component having a frequency of fa or higher in the q-axis target current qi * before correction is canceled out. By setting the predetermined value fa in the self-excited vibration region of the steering system, the influence of the self-excited vibration of the steering system is prevented from reaching the q-axis target current value qi *.

[Effect of Example 1]
(1) In the first embodiment, the pump P that supplies hydraulic pressure, the motor M that drives the pump P, the control unit 10 that outputs a drive command signal to the motor M, and the rotation of the pump P or the motor M A motor rotation speed sensor M / Sen that detects or measures the speed, and a predetermined high-frequency component fluctuation (self-excited vibration region of the steering system) among the rotation speed components of the motor M measured by the motor rotation speed sensor M / Sen. The correction unit 75 corrects the drive command signal so as to cancel.

  As a result, the motor drive signal is corrected so as to cancel out the fluctuation (vibration) in the high-frequency region of the motor rotation speed due to the friction change of the motor M or the pump P, the pump internal pressure change, etc., and the torque T of the motor M overcomes the friction. The vibration in the high frequency region can be suppressed. Further, by performing correction only in the high frequency region, it is possible to cancel the vibration without disturbing a desired change in the rotational speed.

  (2) (3) In the power steering apparatus using the rack and pinion and the hydraulic power steering apparatus using the hydraulic power cylinder, the same operation and effect can be obtained by executing the same control as in (1).

  A second embodiment will be described with reference to FIGS. 9 and 10. Since the basic configuration is the same as that of the first embodiment, only different points will be described. In the first embodiment, a constant value is used for the current conversion coefficient K. However, the second embodiment is different in that K is changed according to the motor rotational speed ω.

  FIG. 9 is a control block diagram of the correction unit 75 in the second embodiment, and FIG. 10 is a map of the current conversion coefficient K.

  When the motor M is rotating at a low speed and a high load, such as when parking, the steering wheel may be caught due to gear distortion or oil film breakage. Therefore, it is desirable to further increase the motor torque in order to apply steering torque against catching at low rotation and high load.

  On the other hand, the moment of inertia of the rotating member increases during high rotation and low load, such as during high-speed steering, so that even if rotation fluctuation of the motor M occurs, the fluctuation is canceled out by the inertia force. Therefore, the correction amount of the rotation fluctuation does not have to be as large as that at the time of low rotation.

  Therefore, the value of the current conversion coefficient K is changed between the low rotation / high load and the high rotation / low load of the motor M, and optimal correction is performed according to the motor rotation speed ω.

The correction unit 75 of the second embodiment includes a low-pass filter LPF in addition to the high-pass filter HPF, and cuts off below a certain rotation speed ωa (> 0) and outputs ωa. At the time of output, the output gain K _LPF is multiplied, and the conversion coefficient K corresponding to the rotation speed ω is read from the current conversion coefficient K-rotation speed ω map.

[Effect of Example 2]
In the second embodiment, the correction unit 75 corrects the drive command signal when the rotational speed ω of the motor M is equal to or less than the predetermined value ωa. As a result, the correction control can be suppressed to the minimum necessary by performing the drive signal correction in the low rotation region where the rotation speed fluctuation is large. Further, it is possible to prevent the influence in the high rotation region due to the correction control.

  A third embodiment will be described with reference to FIG. The basic configuration is the same as that of the first embodiment. The third embodiment is different in that a q-axis target current value qi * is calculated by adding a differential term in order to increase the steering response.

FIG. 11 is a control block diagram of the correction unit 75 in the third embodiment. As in the first embodiment, the output X of the high-pass filter HPF = ω · K _HPF is multiplied by the current conversion coefficient K to calculate K · X.

  In the third embodiment, the difference between the output X and its reciprocal 1 / X is calculated, and this difference X-1 / X is multiplied by a preset differential value conversion coefficient Kd to obtain a differential term Kd (X-1 / X ), The sum of K · X and the derivative term Kd (X−1 / X) is subtracted from the q-axis target current value qi * before correction, and the q-axis target current value qi * after correction is calculated.

  In this way, by advancing the phase using the differential term, it is possible to accurately suppress the vibration in the high frequency region even in an unstable region where a phase delay is likely to occur. In particular, in the case of hydraulic power steering, when the turning speed is fast and the volume change of the cylinder is large, the transmission response seems to be delayed, but vibration suppression can be effectively executed even in such a sudden turning state. .

  A fourth embodiment will be described with reference to FIG. The basic configuration is the same as that of the first embodiment. The correction unit 75 according to the fourth embodiment further includes a sampling unit 75a (learning unit) that learns a periodic decrease in the rotational speed of the motor M, and the occurrence of a periodic decrease in the rotational speed ω learned by the sampling unit 75a. The target current of the motor M is corrected to increase in accordance with the timing.

  FIG. 12 is a control block diagram of the correction unit 75 in the fourth embodiment. The sampling unit 75a receives the phase angle θ of the motor M and the motor rotational speed ω after passing through the high-pass filter HPF.

  When the gear of the pump P is distorted, the pump friction changes at the distorted portion, and this friction change occurs periodically with the rotation of the pump. Since mechanical rotation characteristic fluctuations periodically occur in this way, smoother motor control is performed by learning this periodic friction change and correcting the target current of the motor M.

  Thereby, it is possible to suppress vibrations in the entire frequency region. When vibration suppression in the high frequency region is performed, the protrusion and drop of ω in the high rotation region may be stored intensively. The same applies to the low rotation region.

[Other embodiments]
The best mode for carrying out the present invention has been described based on each embodiment, but the specific configuration of the present invention is not limited to each embodiment and does not depart from the gist of the invention. Such design changes are included in the present invention.

  In the first to fourth embodiments, the q-axis current target value qi * is corrected, but other parameters may be corrected as long as the output of the motor M can be corrected.

  Further, technical ideas other than the claims that can be grasped from the above-described embodiments and examples will be described together with the effects thereof.

(A) In the electric pump device according to claim 1,
The electric pump device, wherein the drive signal correction means further includes a filter circuit for extracting a high frequency component of an output signal from the rotation speed measurement means.

  By extracting only the high frequency component by the filter circuit, only the desired high frequency component can be corrected.

(B) In the electric pump device according to claim 1,
The electric motor is a brushless motor,
The electric pump device characterized in that the rotational speed measuring means is provided in the brushless motor and estimates a rotational speed based on a detection output from a rotational position sensor that detects a rotational position of a rotational shaft of the brushless motor.

  By using the rotational position sensor output provided in the brushless motor, there is no need to provide a separate sensor. Further, since the rotational position sensor detects the rotational position of the rotational shaft of the brushless motor, it is possible to obtain a highly accurate rotational speed signal of the motor.

(C) The electric pump device according to claim 1
Learning means for learning a decrease in the periodic rotation speed of the electric motor;
The electric pump device, wherein the motor control circuit increases and corrects the drive command signal in accordance with a generation timing of a periodic rotational speed decrease learned by the learning unit.

  When the pump gear is distorted, the pump friction changes at the distorted portion, and this friction change is periodically generated as the pump rotates. By learning this periodic friction change and correcting the drive command signal, smoother motor control can be performed.

(D) In the electric pump device according to claim 1,
The electric pump device, wherein the drive signal correcting means gradually decreases or gradually increases the drive command signal so as to cancel the predetermined high-frequency component.

  When the drive signal is corrected, the drive signal is gradually decreased or increased, thereby suppressing a rapid change in the drive signal and suppressing an unnecessary motor torque fluctuation.

(E) In the electric pump device according to claim 1,
The electric pump device characterized in that the drive signal correction amount of the drive signal correction means is suppressed to a predetermined value or less.

  By not providing the drive signal correction amount above a predetermined value, the basic control amount is not corrected more than necessary.

(F) In the electric pump device according to claim 1,
The electric pump device characterized in that the drive signal correction means corrects the drive command signal when the rotation speed of the electric motor is equal to or less than a predetermined value.

  By performing drive signal correction in a low rotation region where the rotational speed fluctuation is large, correction control can be minimized. Further, it is possible to prevent the influence in the high rotation region due to the correction control.

(G) In the power steering device according to claim 2,
The electric motor is a brushless motor,
The power steering device according to claim 1, wherein the rotation speed measuring means is provided in the brushless motor and estimates a rotation speed based on a detection output from a rotation position sensor that detects a rotation position of a rotation shaft of the brushless motor.

  By using the rotational position sensor output provided in the brushless motor, there is no need to provide a separate sensor. Further, since the rotational position sensor detects the rotational position of the rotational shaft of the brushless motor, it is possible to obtain a highly accurate rotational speed signal of the motor.

(H) The power steering device according to claim 2 is:
Learning means for learning a decrease in the periodic rotational speed of the electric motor;
The power control apparatus, wherein the motor control circuit increases and corrects the drive command signal in accordance with a generation timing of a periodic rotational speed learned by the learning unit.

  When the gear of the steering mechanism is distorted, the friction changes at the distorted portion, and the friction change periodically occurs as the gear rotates. By learning this periodic friction change and correcting the drive command signal, smoother motor control can be performed.

(I) In the power steering device according to claim 3,
The electric motor stops rotation at least when the vehicle is in a straight traveling state.

  In a power steering device in which the electric motor switches between rotation and stop, a state where the motor rotation speed is low often occurs, such as at the start of rotation of the electric motor or immediately before stopping, and the pump is likely to be temporarily stopped in such a state. . By performing delay correction in this low-speed rotation state of the motor, it is possible to prevent unintended motor speed fluctuations.

1 is a system configuration diagram of a power steering device in Embodiment 1. FIG. FIG. 3 is a block diagram illustrating a configuration inside a control unit according to the first embodiment. FIG. 3 is a schematic diagram illustrating a configuration of a pump unit according to the first embodiment. It is a figure which shows the flow of the oil at the time of the normal torque assist control in Example 1. FIG. It is operation | movement explanatory drawing which shows a motion of the return check valve in Example 1. FIG. It is a control block diagram of the part used for motor drive in a control unit. It is a control block diagram of a correction | amendment part. FIG. 4 is a diagram showing a relationship between an input frequency and an output gain in a high-pass filter provided in the correction unit. FIG. 10 is a control block diagram of a correction unit in Embodiment 2. 6 is a map of current conversion coefficients in Example 2. FIG. 10 is a control block diagram of a correction unit in Embodiment 3. FIG. 10 is a control block diagram of a correction unit in Embodiment 4.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Steering wheel 2 Steering shaft 4 Fail safe valve 5 Power steering mechanism 5a Power cylinder 8 Warning lamp 10 Control unit 11 Power supply 12 Torque sensor 13 Ignition switch 14 Engine speed sensor 15 Vehicle speed sensor 16 Connector 51, 52 Cylinder chamber 53 Piston 54 Rack Shaft 61 Hydraulic pipe 62 Bypass circuit 63 Drain oil passage 70 Target torque calculation unit 71 Current conversion unit 72 Control unit 73 2-phase-3 phase conversion unit 74 3-phase-2 phase conversion unit 75 Correction unit 75a Sampling unit 101 Power supply circuit Watchdog timer 102 Engine speed processing circuit 103 Torque sensor processing circuit 104 Vehicle speed signal processing circuit 105 Diagnosis circuit 106 Communication circuit 107 Main microcomputer 108 Sub microcomputer 109 Safe relay 111 Fail safe relay diagnostic input circuit 112 Motor drive circuit 112a Output control unit 112b Inverter circuit 113 Current monitor circuit 114 Motor terminal voltage circuit 115 Motor rotation signal processing circuit 116 Fail safe valve drive circuit 117 Warning lamp drive circuit 201a, 201b Check Valves 202a, 202b, 205 Reservoir tank 203 Return check valve 204 Check valve 205 Reservoir tanks 206a, 206b Return springs 207a, 207b Hydraulic chamber 208a, 208b Piston chamber 210 Spool valve M Motor M / Sen Motor rotational speed sensor P Pump

Claims (3)

A pump for supplying hydraulic pressure;
An electric motor for driving the pump;
An electric motor control circuit for outputting a drive command signal to the electric motor;
Rotation speed measuring means for detecting or measuring the rotation speed of the electric motor;
An electric pump device comprising: drive signal correction means for correcting the drive command signal so as to cancel a predetermined high-frequency component fluctuation among rotation speed components measured by the rotation speed measurement means. A steering mechanism connected to the steering wheel;
An electric motor for applying a steering assist torque to the steering mechanism;
Electric motor control means for outputting a drive command signal to the electric motor;
Rotation speed measuring means for detecting or measuring the rotation speed of the electric motor;
Drive signal correction means for correcting the drive command signal so as to cancel a predetermined high-frequency component fluctuation among the rotation speed components measured by the rotation speed measurement means. A hydraulic power cylinder for assisting the steering force of the steering mechanism connected to the steering wheel;
A pump for supplying hydraulic pressure to the pressure chamber of the hydraulic power cylinder;
An electric motor for driving the pump;
A motor control circuit for outputting a drive command signal to the electric motor;
Rotation speed measuring means for detecting or measuring the rotation speed of the electric motor;
Drive signal correction means for correcting the drive command signal so as to cancel a predetermined high-frequency component fluctuation among the rotation speed components measured by the rotation speed measurement means.

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