WO2013183349A1 - Dispositif de commande de véhicule et procédé de commande de véhicule - Google Patents

Dispositif de commande de véhicule et procédé de commande de véhicule Download PDF

Info

Publication number
WO2013183349A1
WO2013183349A1 PCT/JP2013/060587 JP2013060587W WO2013183349A1 WO 2013183349 A1 WO2013183349 A1 WO 2013183349A1 JP 2013060587 W JP2013060587 W JP 2013060587W WO 2013183349 A1 WO2013183349 A1 WO 2013183349A1
Authority
WO
WIPO (PCT)
Prior art keywords
damping force
speed
control
vehicle
wheel
Prior art date
Application number
PCT/JP2013/060587
Other languages
English (en)
Japanese (ja)
Inventor
宏信 菊池
昌明 縄野
Original Assignee
日産自動車株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日産自動車株式会社 filed Critical 日産自動車株式会社
Publication of WO2013183349A1 publication Critical patent/WO2013183349A1/fr

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/06—Characteristics of dampers, e.g. mechanical dampers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
    • B60G2400/25—Stroke; Height; Displacement
    • B60G2400/252—Stroke; Height; Displacement vertical
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
    • B60G2400/90—Other conditions or factors
    • B60G2400/91—Frequency
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2500/00—Indexing codes relating to the regulated action or device
    • B60G2500/10—Damping action or damper

Definitions

  • the present invention relates to a control device and a control method for controlling the state of a vehicle.
  • Patent Document 1 discloses a technique for estimating the stroke speed from the fluctuation of the wheel speed in a predetermined frequency region and changing the damping force of the damping force variable shock absorber according to the stroke speed to control the sprung behavior. .
  • an object of the present invention is to provide a vehicle control device and a control method capable of achieving stabilization of the vehicle body posture when the estimated accuracy of stroke speed is reduced.
  • the damping force is variable based on the stroke speed. While calculating the damping force control amount of the shock absorber, if a decrease in estimated accuracy is detected, the damping force control amount is calculated according to the vehicle speed, and the size of the wheel friction circle is less than the predetermined value.
  • the damping force control amount corresponding to the vehicle speed is set to be larger than the damping force control amount corresponding to the vehicle speed when it is larger than the predetermined value.
  • FIG. 1 is a system schematic diagram illustrating a vehicle control apparatus according to a first embodiment.
  • FIG. 2 is a control block diagram illustrating a control configuration of the vehicle control device according to the first embodiment.
  • 1 is a conceptual diagram illustrating a configuration of a wheel speed feedback control system according to a first embodiment.
  • FIG. 3 is a control block diagram illustrating a configuration of a traveling state estimation unit according to the first embodiment. It is a control block diagram showing the control content in the stroke speed calculating part of Example 1.
  • FIG. 3 is a block diagram illustrating a configuration of a reference wheel speed calculation unit according to the first embodiment. It is the schematic showing a vehicle body vibration model. It is a control block diagram showing brake pitch control of Example 1.
  • FIG. 3 is a control block diagram illustrating a configuration of roll rate suppression control according to the first embodiment. 3 is a time chart illustrating an envelope waveform forming process of roll rate suppression control according to the first embodiment.
  • FIG. 3 is a block diagram illustrating a control configuration of unsprung vibration suppression control according to the first embodiment.
  • FIG. 3 is a control block diagram illustrating a control configuration of a damping force control unit according to the first embodiment.
  • 6 is a flowchart illustrating attenuation coefficient arbitration processing in a standard mode according to the first embodiment.
  • 6 is a flowchart illustrating an attenuation coefficient arbitration process in the sport mode according to the first embodiment.
  • 6 is a flowchart illustrating attenuation coefficient arbitration processing in the comfort mode according to the first embodiment.
  • 6 is a flowchart illustrating attenuation coefficient arbitration processing in a highway mode according to the first exemplary embodiment.
  • FIG. 6 is a flowchart illustrating a mode selection process based on a running state in an attenuation coefficient arbitration unit according to the first embodiment.
  • FIG. 6 is a control block diagram illustrating a control configuration of a vehicle control device according to a second embodiment.
  • FIG. 3 is a control block diagram illustrating a configuration of a control unit at the time of detection of a decrease in estimated accuracy according to the first embodiment. It is explanatory drawing showing the setting method of the attenuation coefficient at the time of the estimation accuracy fall in the attenuation coefficient setting part of Example 1.
  • FIG. 6 is a flowchart illustrating a mode selection process based on a running state in an attenuation coefficient arbitration unit according to the first embodiment.
  • FIG. 6 is a control block diagram illustrating a control configuration of a vehicle control device according to a second embodiment.
  • FIG. 3 is a control block diagram illustrating a configuration of a control unit at the time of detection of a decrease in estimated accuracy according to the first embodiment. It
  • FIG. 1 is a system schematic diagram illustrating a vehicle control apparatus according to the first embodiment.
  • the vehicle includes an engine 1 that is a power source and a brake 20 that generates braking torque due to friction force on each wheel (hereinafter, when displaying brakes corresponding to individual wheels, right front wheel brake: 20FR, left front wheel brake: 20FL).
  • S / A shock absorber 3
  • the engine 1 includes an engine controller (hereinafter also referred to as an engine control unit, which corresponds to power source control means) 1a that controls torque output from the engine 1, and the engine controller 1a is configured to By controlling the fuel injection amount, ignition timing, etc., the desired engine operating state (engine speed and engine output torque) is controlled. Further, the brake 20 generates a braking torque based on the hydraulic pressure supplied from the brake control unit 2 that can control the brake hydraulic pressure of each wheel according to the traveling state.
  • the brake control unit 2 includes a brake controller (hereinafter also referred to as a brake control unit) 2a for controlling a braking torque generated by the brake 20, and a master cylinder pressure generated by a driver's brake pedal operation or a built-in motor.
  • a pump pressure generated by the drive pump is used as a hydraulic pressure source, and a desired hydraulic pressure is generated in the brake 20 of each wheel by opening and closing operations of a plurality of solenoid valves.
  • the S / A3 is a damping force generator that attenuates the elastic motion of a coil spring provided between a vehicle unsprung (axle, wheel, etc.) and a sprung (vehicle body, etc.). It is configured to be variable.
  • the S / A 3 includes a cylinder in which fluid is sealed, a piston that strokes in the cylinder, and an orifice that controls fluid movement between fluid chambers formed above and below the piston. Furthermore, orifices having a plurality of types of orifice diameters are formed in the piston, and an orifice corresponding to a control command is selected from the plurality of types of orifices when the S / A actuator is operated. Thereby, the damping force according to the orifice diameter can be generated. For example, if the orifice diameter is small, the movement of the piston is easily restricted, so that the damping force is high. If the orifice diameter is large, the movement of the piston is difficult to be restricted, and thus the damping force is small.
  • an electromagnetic control valve is arranged on the communication path connecting fluids formed above and below the piston, and the damping force is set by controlling the opening / closing amount of the electromagnetic control valve.
  • the S / A 3 has an S / A controller 3a (corresponding to damping force control means) that controls the damping force of the S / A 3, and controls the damping force by operating the orifice diameter by the S / A actuator.
  • a wheel speed sensor 5 for detecting the wheel speed of each wheel (hereinafter, when displaying the wheel speed corresponding to each wheel, right front wheel speed: 5FR, left front wheel speed: 5FL, right rear wheel speed: 5RR. , Left rear wheel speed: 5RL)), an integrated sensor 6 for detecting longitudinal acceleration, yaw rate and lateral acceleration acting on the center of gravity of the vehicle, and a steering angle which is a steering operation amount of the driver is detected.
  • Steering angle sensor 7 vehicle speed sensor 8 for detecting vehicle speed
  • engine torque sensor 9 for detecting engine torque
  • engine speed sensor 10 for detecting engine speed
  • master pressure sensor 11 for detecting master cylinder pressure.
  • a brake switch 12 that outputs an on-state signal when the brake pedal is operated, an accelerator opening sensor 13 that detects an accelerator pedal opening, and an outside air temperature A temperature sensor 14 for detecting a.
  • the signals from these various sensors are input to the engine controller 1a, the brake controller 2a, and the S / A controller 3a as necessary.
  • the arrangement of the integrated sensor 6 may be at the center of gravity of the vehicle, or may be any place other than that as long as various values at the center of gravity can be estimated. Moreover, it is not necessary to be an integral type, and a configuration in which yaw rate, longitudinal acceleration, and lateral acceleration are individually detected may be employed.
  • the control amount by the engine 1 and the brake 20 is limited and output from the control amount that can be actually output, thereby reducing the burden on the S / A 3 and accompanying the control of the engine 1 and the brake 20. Suppresses discomfort that occurs.
  • Skyhook control is performed by all actuators. At this time, without using a stroke sensor or a sprung vertical acceleration sensor generally required for skyhook control, the skyhook control can be performed with an inexpensive configuration using wheel speed sensors mounted on all vehicles. Realize.
  • scalar control frequency sensitive control
  • FIG. 2 is a control block diagram illustrating a control configuration of the vehicle control apparatus according to the first embodiment.
  • the controller includes an engine controller 1a, a brake controller 2a, and an S / A controller 3a, and each controller constitutes a wheel speed feedback control system.
  • estimation that is the probability of state estimation of each of the traveling state estimation units (first traveling state estimation unit 100, second traveling state estimation unit 200, and third traveling state estimation unit 32) described later.
  • An estimated accuracy decrease detection unit 4a that detects a decrease in accuracy
  • an estimated accuracy decrease detection time control unit 5a that transitions to an appropriate control state when a decrease in estimated accuracy is detected.
  • the configuration including three controllers as the controller is shown, but each controller may be configured from one integrated controller without any particular limitation.
  • the configuration including the three controllers in the first embodiment is that the engine controller and the brake controller in the existing vehicle are used as they are to form the engine control unit 1a and the brake control unit 2a, and the S / A controller 3a is separately mounted.
  • the vehicle control apparatus of the first embodiment is realized.
  • the engine controller 1a mainly uses the wheel speed detected by the wheel speed sensor 5 to determine the stroke speed, bounce rate, roll rate and pitch of each wheel used for the skyhook control of the sprung mass damping control unit 101a described later.
  • a first running state estimation unit 100 that estimates the rate, an engine posture control unit 101 that calculates an engine posture control amount that is an engine torque command, and controls the operating state of the engine 1 based on the calculated engine posture control amount.
  • An engine control unit 102 The details of the estimation process of the first traveling state estimation unit 100 will be described later.
  • the engine attitude control unit 101 includes a sprung mass damping control unit 101a that calculates a sprung control amount that suppresses bounce motion and pitch motion by skyhook control, and ground load variation suppression that suppresses ground load variation of front and rear wheels.
  • a ground load control unit 101b that calculates a control amount
  • an engine-side driver input control unit 101c that calculates a yaw response control amount corresponding to a vehicle behavior that the driver wants to achieve based on signals from the steering angle sensor 7 and the vehicle speed sensor 8 And have.
  • the engine attitude control unit 101 calculates an engine attitude control amount that minimizes the control amount calculated by each of these control units by optimal control (LQR), and determines the final engine attitude control amount for the engine control unit 102. Output.
  • LQR optimal control
  • the S / A 3 can reduce the damping force control amount, and therefore, deterioration of the high frequency vibration can be avoided. Moreover, since S / A3 can concentrate on suppression of roll motion, it can suppress roll motion effectively.
  • the brake controller 2a Based on the wheel speed detected by the wheel speed sensor 5, the brake controller 2a estimates the stroke speed and pitch rate of each wheel, and the like based on the estimated stroke speed and pitch rate.
  • Skyhook control unit 201 (details will be described later) that calculates a brake attitude control amount based on skyhook control, and brake control unit 202 that controls the braking torque of brake 20 based on the calculated brake attitude control amount And have.
  • the same estimation process is adopted as the estimation process in the first traveling state estimation unit 100 and the second traveling state estimation unit 200, but other estimation processes are performed as long as the process is estimated from the wheel speed. It may be used.
  • the S / A controller 3a includes a driver input control unit 31 that performs driver input control for achieving a desired vehicle posture based on a driver's operation (steering operation, accelerator operation, brake pedal operation, etc.), and detection values of various sensors.
  • a third traveling state estimation unit 32 that estimates the traveling state based on (mainly the wheel speed sensor value of the wheel speed sensor 5), and a sprung mass damping that controls the vibration state on the spring based on the estimated traveling state
  • a control unit 33 an unsprung vibration suppression control unit 34 that controls the unsprung vibration state based on the estimated traveling state, a shock absorber attitude control amount output from the driver input control unit 31, and a sprung mass damping
  • a damping force to be set in the S / A 3 is determined.
  • a damping force control unit 35 for performing the damping force control of the A.
  • the same estimation process is adopted as the estimation process in the first traveling state estimation unit 100, the second traveling state estimation unit 200, and the third traveling state estimation unit 32, but the process is estimated from the wheel speed. If so, other estimation processes may be used and there is no particular limitation.
  • FIG. 3 is a conceptual diagram showing the configuration of the wheel speed feedback control system of the first embodiment.
  • the engine 1, the brake 20 and the S / A 3 individually constitute an engine feedback control system, a brake feedback control system, and an S / A feedback control system.
  • control interference becomes a problem.
  • the effects of the control of each actuator appear as wheel speed fluctuations, by configuring the wheel speed feedback control system, the effect of each actuator is monitored as a result, and control interference is avoided. It is. For example, if a certain sprung vibration is suppressed by the engine 1, the wheel speed fluctuation
  • the brake 20 and the S / A 3 perform control based on the wheel speed in which the influence is reflected.
  • the feedback control system is configured using a common value of wheel speed, even if individual control is performed without controllable mutual monitoring, as a result, control based on mutual monitoring (below)
  • This control is described as cooperative control), and the vehicle posture can be converged in the stabilization direction.
  • each feedback control system will be described sequentially.
  • the 1st, 2nd, 3rd driving state estimation part which is a common structure provided in each feedback control system is demonstrated.
  • the same estimation process is adopted as the estimation process in the first traveling state estimation unit 100, the second traveling state estimation unit 200, and the third traveling state estimation unit 32. Therefore, since the process in each estimation part is common, the estimation process in the 3rd driving state estimation part 32 is demonstrated as a representative.
  • Each of the running state estimation units may be provided with a separate estimation model as long as it is a state estimation using the wheel speed, and is not particularly limited.
  • FIG. 4 is a control block diagram showing the configuration of the third traveling state estimation unit of the first embodiment.
  • the stroke of each wheel used for the skyhook control of the sprung mass damping control unit 33 to be described later is basically based on the wheel speed detected by the wheel speed sensor 5. Calculate speed, bounce rate, roll rate and pitch rate. First, the value of the wheel speed sensor 5 of each wheel is input to the stroke speed calculation unit 321, and the sprung speed is calculated from the stroke speed of each wheel calculated by the stroke speed calculation unit 321.
  • FIG. 5 is a control block diagram showing the control contents in the stroke speed calculation unit of the first embodiment.
  • the stroke speed calculation unit 321 is individually provided for each wheel, and the control block diagram shown in FIG. 5 is a control block diagram focusing on a certain wheel.
  • the value of the wheel speed sensor 5, the front wheel rudder angle ⁇ f detected by the rudder angle sensor 7, and the rear wheel rudder angle ⁇ r (if a rear wheel steering device is provided, the actual rear wheel rudder)
  • the reference wheel speed calculation unit 300 that calculates a reference wheel speed based on the vehicle body lateral speed and the actual yaw rate detected by the integrated sensor 6 may be used.
  • a tire rotation vibration frequency calculation unit 321a that calculates the tire rotation vibration frequency based on the calculated reference wheel speed, and a deviation calculation unit 321b that calculates a deviation (wheel speed fluctuation) between the reference wheel speed and the wheel speed sensor value;
  • the GEO conversion unit 321c that converts the deviation calculated by the deviation calculation unit 321b into a suspension stroke amount, the stroke speed calibration unit 321d that calibrates the converted stroke amount to the stroke speed, and the stroke speed calibration unit 321d
  • a signal processing unit 321e that applies a band elimination filter corresponding to the frequency calculated by the tire rotation vibration frequency calculation unit 321a to remove a tire rotation primary vibration component and calculates a final stroke speed.
  • FIG. 6 is a block diagram illustrating a configuration of a reference wheel speed calculation unit according to the first embodiment.
  • the reference wheel speed refers to a value obtained by removing various disturbances from each wheel speed.
  • the difference between the wheel speed sensor value and the reference wheel speed is a value related to a component that fluctuates according to the stroke generated by the bounce behavior, roll behavior, pitch behavior, or unsprung vertical vibration of the vehicle body.
  • the stroke speed is estimated based on this difference.
  • the plane motion component extraction unit 301 receives the wheel speed sensor value as input and calculates the first wheel speed V0 that is the reference wheel speed of each wheel based on the vehicle body plan view model.
  • the wheel speed sensor value detected by the wheel speed sensor 5 is ⁇ (rad / s)
  • the front wheel actual steering angle detected by the steering angle sensor 7 is ⁇ f (rad)
  • the rear wheel actual steering angle is ⁇ r (rad )
  • the vehicle body lateral speed is Vx
  • the yaw rate detected by the integrated sensor 6 is ⁇ (rad / s)
  • the vehicle speed estimated from the calculated reference wheel speed ⁇ 0 is V (m / s)
  • the reference to be calculated Wheel speed is VFL, VFR, VRL, VRR
  • front wheel tread is Tf
  • rear wheel tread is Tr
  • distance from vehicle center of gravity to front wheel is Lf
  • distance from vehicle center of gravity to rear wheel is Lr.
  • VFL (V-Tf / 2 ⁇ ⁇ ) cos ⁇ f + (Vx + Lf ⁇ ⁇ ) sin ⁇ f
  • VFR (V + Tf / 2 ⁇ ⁇ ) cos ⁇ f + (Vx + Lf ⁇ ⁇ ) sin ⁇ f
  • VRL (V ⁇ Tr / 2 ⁇ ⁇ ) cos ⁇ r + (Vx ⁇ Lr ⁇ ⁇ ) sin ⁇ r
  • VRR (V + Tr / 2 ⁇ ⁇ ) cos ⁇ r + (Vx-Lr ⁇ ⁇ ) sin ⁇ r
  • V is described as V0FL, V0FR, V0RL, V0RR (corresponding to the first wheel speed) as a value corresponding to each wheel.
  • V0FL ⁇ VFL-Lf ⁇ ⁇ sin ⁇ f ⁇ / cos ⁇ f + Tf / 2 ⁇ ⁇
  • V0FR ⁇ VFR-Lf ⁇ ⁇ sin ⁇ f ⁇ / cos ⁇ f-Tf / 2 ⁇ ⁇
  • V0RL ⁇ VRL + Lr ⁇ ⁇ sin ⁇ r ⁇ / cos ⁇ r + Tr / 2 ⁇ ⁇
  • V0RR ⁇ VRR + Lf ⁇ ⁇ sin ⁇ f ⁇ / cos ⁇ r-Tr / 2 ⁇ ⁇
  • the roll disturbance removing unit 302 calculates the second wheel speeds V0F and V0R that are the reference wheel speeds of the front and rear wheels based on the vehicle body front view model with the first wheel speed V0 as an input.
  • the vehicle body front view model removes the wheel speed difference caused by the roll motion that occurs around the roll rotation center on the vertical line passing through the center of gravity of the vehicle when the vehicle is viewed from the front. Is done.
  • V0F (V0FL + V0FR) / 2
  • V0R (V0RL + V0RR) / 2
  • the second wheel speeds V0F and V0R from which disturbance based on the roll is removed are obtained.
  • the pitch disturbance removal unit 303 calculates the third wheel speeds VbFL, VbFR, VbRL, and VbRR that are the reference wheel speeds of all the wheels based on the vehicle body side view model with the second wheel speeds V0F and V0R as inputs.
  • the vehicle body side view model is to remove the wheel speed difference caused by the pitch motion generated around the pitch rotation center on the vertical line passing through the center of gravity of the vehicle when the vehicle is viewed from the lateral direction. It is expressed by the following formula.
  • the stroke speed calculation unit 321 calculates the stroke speeds Vz_sFL, Vz_sFR, Vz_sRL, and Vz_sRR for each wheel by the above processing
  • the sprung speed calculation unit 322 performs bounce rate, roll rate, and pitch rate for skyhook control. Calculated.
  • Skyhook control is to achieve a flat running state by setting a damping force based on the relationship between the S / A3 stroke speed and the sprung speed, and controlling the posture on the sprung.
  • the value that can be detected from the wheel speed sensor 5 is the stroke speed, and since the vertical acceleration sensor or the like is not provided on the spring, the sprung speed needs to be estimated using an estimation model.
  • the problem of the estimation model and the model configuration to be adopted will be described.
  • FIG. 7 is a schematic diagram showing a vehicle body vibration model.
  • FIG. 7A is a model of a vehicle (hereinafter referred to as a conveyor vehicle) having an S / A with a constant damping force
  • FIG. 7B has an S / A having a variable damping force.
  • Ms represents the mass on the spring
  • Mu represents the mass below the spring
  • Ks represents the elastic coefficient of the coil spring
  • Cs represents the damping coefficient of S / A
  • Ku represents the unsprung (tire).
  • Cu represents an unsprung (tire) damping coefficient
  • Cv represents a variable damping coefficient
  • Z2 represents a position on the spring
  • z1 represents a position under the spring
  • z0 represents a road surface position.
  • Changing the damping force basically means changing the force that limits the piston moving speed of S / A 3 in accordance with the suspension stroke. Since the semi-active S / A3 that cannot positively move the piston in the desired direction is used, when the semi-active skyhook model is employed and the sprung speed is obtained, it is expressed as follows.
  • the magnitude of the estimated sprung speed is smaller than the actual value in the frequency band below the sprung resonance, but the most important in skyhook control is the phase. If the correspondence between the phase and the sign can be maintained, the skyhook can be maintained. Since control is achieved and the magnitude of the sprung speed can be adjusted by other factors, there is no problem.
  • the sprung speed can be estimated if the stroke speed of each wheel is known.
  • the actual vehicle is four wheels instead of one wheel, it is considered to estimate the state of the spring by mode decomposition into roll rate, pitch rate and bounce rate using the stroke speed of each wheel. To do.
  • the above three components are calculated from the stroke speed of the four wheels, one corresponding component is insufficient, and the solution becomes indefinite. Therefore, a war plate representing the movement of the diagonal wheels is introduced.
  • the stroke amount bounce term is xsB
  • the roll term is xsR
  • the pitch term is xsP
  • the warp term is xsW
  • the stroke amount corresponding to Vz_sFL, Vz_sFR, Vz_sRL, Vz_sRR is z_sFL, z_sFR, z_sRL, z_sRR, Holds.
  • dxsB 1/4 (Vz_sFL + Vz_sFR + Vz_sRL + Vz_sRR)
  • dxsR 1/4 (Vz_sFL-Vz_sFR + Vz_sRL-Vz_sRR)
  • dxsP 1/4 (-Vz_sFL-Vz_sFR + Vz_sRL + Vz_sRR)
  • dxsW 1/4 (-Vz_sFL + Vz_sFR + Vz_sRL-Vz_sRR)
  • the vehicle control apparatus includes the engine 1, the brake 20, and the S / A 3 as actuators for achieving sprung posture control.
  • the sprung mass damping control unit 101a in the engine controller 1a has two bounce rate and pitch rate as control targets
  • the sky hook control unit 201 in the brake controller 2a has pitch rate as control targets.
  • the skyhook control unit 33a in the controller 3a three of bounce rate, roll rate, and pitch rate are controlled.
  • the bounce direction skyhook control amount FB is calculated as a part of the engine attitude control amount in the sprung mass damping control unit 101a.
  • the skyhook control unit 33a calculates as a part of the S / A attitude control amount.
  • the skyhook control amount FR in roll direction is calculated as part of the S / A attitude control amount in the sky hook control unit 33a.
  • the sky hook control amount FP in the pitch direction is calculated as a part of the engine attitude control amount in the sprung mass damping control unit 101a.
  • the skyhook control unit 201 calculates the brake attitude control amount.
  • the skyhook control unit 33a calculates as a part of the S / A attitude control amount.
  • the engine attitude control unit 101 is set with a limit value for limiting the engine torque control amount according to the engine attitude control amount so as not to give the driver a sense of incongruity.
  • the engine torque control amount is limited to be within a predetermined longitudinal acceleration range when converted to longitudinal acceleration. Therefore, when the engine attitude control amount (engine torque control amount) is calculated based on FB or FP and a value equal to or greater than the limit value is calculated, bounce rate or pitch rate skyhook control that can be achieved by the limit value
  • the engine attitude control amount is output as a quantity.
  • the engine control unit 102 calculates an engine torque control amount based on the engine attitude control amount corresponding to the limit value, and outputs the engine torque control amount to the engine 1.
  • the skyhook control unit 201 is set with a limit value for limiting the braking torque control amount so as not to give the driver a sense of incongruity as in the engine 1 (details of the limit value will be described later).
  • the braking torque control amount is converted into the longitudinal acceleration, the braking torque control amount is limited to be within a predetermined longitudinal acceleration range (a limit value obtained from the occupant's uncomfortable feeling, the life of the actuator, etc.). Therefore, when the brake attitude control amount is calculated based on the FP and a value equal to or greater than the limit value is calculated, a pitch rate suppression amount (hereinafter referred to as a brake attitude control amount) that can be achieved by the limit value.
  • a pitch rate suppression amount hereinafter referred to as a brake attitude control amount
  • the brake control unit 202 calculates a braking torque control amount (or deceleration) based on the brake attitude control amount corresponding to the limit value, and outputs it to the brake 20.
  • FIG. 8 is a control block diagram showing the brake pitch control of the first embodiment.
  • the vehicle body mass is m
  • the front wheel braking force is BFf
  • the rear wheel braking force is BFr
  • the height between the vehicle center of gravity and the road surface is Hcg
  • the vehicle acceleration is a
  • the pitch moment is Mp
  • the pitch rate is Vp.
  • the brake attitude control amount calculation unit 334 is composed of the following control blocks.
  • the dead zone processing code determination unit 3341 determines the sign of the input pitch rate Vp, and when it is positive, it outputs 0 to the deceleration reduction processing unit 3342 because control is unnecessary, and when it is negative, it determines that control is possible.
  • the pitch rate signal is output to the deceleration reduction processing unit 3342.
  • the deceleration feeling reduction process is a process corresponding to the limitation by the limit value performed in the brake attitude control amount calculation unit 334.
  • the square processor 3342a squares the pitch rate signal. This inverts the sign and smoothes the rise of the control force.
  • the pitch rate square decay moment calculation unit 3342b calculates the pitch moment Mp by multiplying the squared pitch rate by the skyhook gain CskyP of the pitch term considering the square process.
  • the target deceleration calculating unit 3342c calculates the target deceleration by dividing the pitch moment Mp by the mass m and the height Hcg between the vehicle center of gravity and the road surface.
  • the calculated rate of change of the target deceleration that is, whether the jerk is within a preset range of the deceleration jerk threshold and the extraction jerk threshold, and the target deceleration is the longitudinal acceleration limit value. Judgment is made whether or not it is within the range. If any threshold is exceeded, the target deceleration is corrected to a value within the jerk threshold range, and if the target deceleration exceeds the limit value, the limit is set. Set within the value. Thereby, the deceleration can be generated so as not to give the driver a sense of incongruity.
  • the target pitch moment conversion unit 3343 calculates the target pitch moment by multiplying the target deceleration limited by the jerk threshold limiting unit 3342d by the mass m and the height Hcg, and outputs the target pitch moment to the brake control unit 2a.
  • the sprung speed is estimated based on the detection value of the wheel speed sensor 5 and the skyhook control is performed based on the estimated sprung speed control.
  • a comfortable driving state (a comfortable ride feeling softer than the vehicle body flatness) is guaranteed.
  • vector control where the relationship (phase, etc.) of the sign of stroke speed and sprung speed is important, such as skyhook control, may make it difficult to achieve proper control due to a slight phase shift. Therefore, we decided to introduce frequency-sensitive control, which is sprung mass damping control according to the scalar quantity of vibration characteristics.
  • FIG. 9 is a diagram in which the wheel speed frequency characteristic detected by the wheel speed sensor and the stroke frequency characteristic of a stroke sensor not mounted in the embodiment are simultaneously written.
  • the frequency characteristic is a characteristic in which the vertical axis represents the magnitude of the amplitude with respect to the frequency as a scalar quantity. Comparing the frequency component of the wheel speed sensor 5 with the frequency component of the stroke sensor, it can be understood that substantially the same scalar amount is taken from the sprung resonance frequency component to the unsprung resonance frequency component. Therefore, the damping force is set based on this frequency characteristic among the detection values of the wheel speed sensor 5.
  • the area where the sprung resonance frequency component exists is felt as if the occupant was thrown into the air by swinging the entire body of the occupant, in other words, the feeling that the gravitational acceleration acting on the occupant was reduced.
  • the frequency region that brings about the waving region (0.5 to 3 Hz), and the region between the sprung resonance frequency component and the unsprung resonance frequency component is not a feeling that gravitational acceleration decreases.
  • the feeling that the human body jumps in small increments when performing (trot), in other words, the frequency range that brings up and down movement that the whole body can follow is the leopard region (3 to 6 Hz), and the region where the unsprung resonance frequency component exists Is not a vertical movement until the mass of the human body follows, but a bull region (6 to 6) is used as a frequency region where vibration is transmitted to a part of the body such as the occupant's thigh. 23 Hz).
  • FIG. 10 is a control block diagram illustrating frequency sensitive control in the sprung mass damping control of the first embodiment.
  • the band elimination filter 350 cuts noise other than the vibration component used for the present control from the wheel speed sensor value.
  • the predetermined frequency region dividing unit 351 divides the frequency region into a frequency region, a lateral region, and a bull region.
  • the Hilbert transform processing unit 352 performs Hilbert transform on each divided frequency band, and converts the frequency band into a scalar quantity based on the frequency amplitude (specifically, an area calculated from the amplitude and the frequency band).
  • the vehicle vibration system weight setting unit 353 sets weights at which vibrations in the frequency bands of the fur region, the leopard region, and the bull region are actually propagated to the vehicle.
  • the human sense weight setting unit 354 sets weights at which vibrations in the frequency bands of the fur region, the leopard region, and the bull region are propagated to the occupant.
  • FIG. 11 is a correlation diagram showing human sensory characteristics with respect to frequency.
  • the occupant's sensitivity is relatively low with respect to the frequency, and the sensitivity gradually increases as the frequency shifts to the high frequency region.
  • the high frequency region above the bull region becomes difficult to be transmitted to the occupant.
  • the human sense weight Wf of the wafe area is set to 0.17
  • the human sense weight Wh of the leopard area is set to 0.34 which is larger than Wf
  • the human sense weight Wb of the bull area is larger than Wf and Wh. Set to 0.38.
  • the weight determination means 355 calculates the ratio of the weights of the respective frequency bands to the weights of the respective frequency bands. If the weight of the wing area is a, the weight of the leopard area is b, and the weight of the bull area is c, the weight coefficient of the wing area is (a / (a + b + c)), and the weight coefficient of the leap area is (b / (a + b + c). )), And the weighting factor of the bull area is (c / (a + b + c)).
  • the scalar amount calculation unit 356 multiplies the scalar amount of each frequency band calculated by the Hilbert transform processing unit 352 by the weight calculated by the weight determination unit 355, and outputs the final scalar amount. The processing so far is performed on the wheel speed sensor value of each wheel.
  • the maximum value selection unit 357 selects the maximum value from the final scalar amount calculated for each of the four wheels. Note that 0.01 in the lower part is set to avoid the denominator becoming 0 because the sum of the maximum values is used as the denominator in the subsequent processing.
  • the ratio calculation unit 358 calculates the ratio using the sum of the scalar value maximum values in each frequency band as the denominator and the scalar value maximum value in the frequency band corresponding to the waving region as the numerator. In other words, the mixing ratio (hereinafter simply referred to as the ratio) of the wafer region included in all vibration components is calculated.
  • the sprung resonance filter 359 performs filter processing of about 1.2 Hz of the sprung resonance frequency with respect to the calculated ratio, and extracts a sprung resonance frequency band component representing a waft region from the calculated ratio. In other words, since the wing area exists at about 1.2 Hz, the ratio of this area is considered to change at about 1.2 Hz. Then, the finally extracted ratio is output to the damping force control unit 35, and a frequency sensitive damping force control amount corresponding to the ratio is output.
  • FIG. 12 is a characteristic diagram showing the relationship between the vibration mixing ratio in the waft region and the damping force by the frequency sensitive control of the first embodiment.
  • the vibration level of sprung resonance is reduced by setting the damping force high when the ratio of the wing area is large.
  • the damping force is set high, the ratio of the leopard area and the bull area is small, so that high frequency vibration or vibration that moves with the leopard is not transmitted to the occupant.
  • the damping force is set low, so that the vibration transmission characteristic more than the sprung resonance is reduced, the high frequency vibration is suppressed, and a smooth riding comfort is obtained.
  • FIG. 13 is a diagram showing the wheel speed frequency characteristics detected by the wheel speed sensor 5 under a certain traveling condition. This is a characteristic that appears particularly when traveling on a road surface in which small unevenness such as a stone pavement continues.
  • the damping force is determined by the value of the amplitude peak in Skyhook control. There is a problem that a very high damping force is set at an incorrect timing and high-frequency vibration is deteriorated.
  • the S / A side driver input control unit 31 calculates a driver input damping force control amount corresponding to a vehicle behavior that the driver wants to achieve based on signals from the steering angle sensor 7 and the vehicle speed sensor 8, and a damping force control unit 35. Output for. For example, when the driver is turning, if the nose side of the vehicle is lifted, the driver's field of view easily deviates from the road surface. In this case, the four-wheel damping force is used as a driver input damping force to prevent the nose from rising. Output as a controlled variable. In addition, a driver input damping force control amount that suppresses a roll generated during turning is output.
  • FIG. 14 is a control block diagram illustrating the configuration of roll rate suppression control according to the first embodiment.
  • the lateral acceleration estimation unit 31b1 estimates the lateral acceleration Yg based on the front wheel steering angle ⁇ f detected by the steering angle sensor 7 and the vehicle speed VSP detected by the vehicle speed sensor 8.
  • A is a predetermined value.
  • the 90 ° phase advance component creation unit 31b2 differentiates the estimated lateral acceleration Yg and outputs a lateral acceleration differential value dYg.
  • the first addition unit 31b4 adds the lateral acceleration Yg and the lateral acceleration differential value dYg.
  • the 90 ° phase delay component creation unit 31b3 outputs a component F (Yg) obtained by delaying the phase of the estimated lateral acceleration Yg by 90 °.
  • the second adder 31b5 adds F (Yg) to the value added by the first adder 31b4.
  • the Hilbert transform unit 31b6 calculates a scalar quantity based on the envelope waveform of the added value.
  • the gain multiplication unit 31b7 multiplies the scalar amount based on the envelope waveform by the gain, calculates a driver input attitude control amount for roll rate suppression control, and outputs the calculated value to the damping force control unit 35.
  • FIG. 15 is a time chart showing the envelope waveform forming process of the roll rate suppression control of the first embodiment.
  • phase delay component F (Yg) If the phase delay component F (Yg) is not added, the damping force from the time t2 to the time t3 is set to a small value, which may cause the vehicle behavior to become unstable due to the roll rate resonance component. In order to suppress this roll rate resonance component, a 90 ° phase delay component F (Yg) is added.
  • FIG. 16 is a block diagram illustrating a control configuration of unsprung vibration suppression control according to the first embodiment.
  • the unsprung resonance component extraction unit 341 extracts a unsprung resonance component by applying a bandpass filter to the wheel speed fluctuation output from the deviation calculation unit 321b in the traveling state estimation unit 32.
  • the unsprung resonance component is extracted from the region of approximately 10 to 20 Hz of the wheel speed frequency component.
  • the envelope waveform shaping unit 342 scalarizes the extracted unsprung resonance component and shapes the envelope waveform using the EnvelopeFilter.
  • the gain multiplication unit 343 multiplies the scalarized unsprung resonance component by a gain, calculates the unsprung damping damping force control amount, and outputs the calculated amount to the damping force control unit 35.
  • the unsprung resonance component is extracted by applying a bandpass filter to the wheel speed fluctuation output from the deviation calculating section 321b in the running state estimating section 32.
  • the unsprung resonance component may be extracted by applying a bandpass filter to the driving force, or the unsprung resonance component may be extracted by the running state estimation unit 32 by estimating and calculating the unsprung speed along with the sprung speed. Good.
  • FIG. 17 is a control block diagram illustrating a control configuration of the damping force control unit according to the first embodiment.
  • the driver input damping force control amount output from the driver input control unit 31 the S / A attitude control amount output from the skyhook control unit 33a, and the frequency sensitive control unit 33b output
  • the frequency sensitive damping force control amount, the unsprung damping damping force control amount output from the unsprung damping control unit 34, and the stroke speed calculated by the running state estimation unit 32 are input, and these values are equivalent. Convert to viscous damping coefficient.
  • each damping coefficient is referred to as driver input damping coefficient k1, S / A attitude damping coefficient k2, frequency sensitive damping coefficient k3, unsprung). (Which is described as damping damping coefficient k4)), which arbitration is performed based on which damping coefficient is controlled, and a final damping coefficient is output.
  • the control signal converter 35c converts the control signal (command current value) for S / A3 based on the attenuation coefficient and stroke speed adjusted by the attenuation coefficient adjuster 35b, and outputs the control signal to S / A3.
  • the vehicle control apparatus has four control modes. First, the standard mode assuming a state where an appropriate turning state can be obtained while driving in a general urban area, and second, a state where a stable turning state can be obtained while actively driving a winding road etc.
  • Comfort mode control mode with the lowest upper limit of the damping force control range
  • This is a highway mode that assumes a state of traveling at a high vehicle speed.
  • priority is given to unsprung vibration suppression control by the unsprung vibration suppression control unit 34 while performing skyhook control by the skyhook control unit 33a.
  • priority is given to driver input control by the driver input control unit 31, and skyhook control by the skyhook control unit 33a and unsprung vibration suppression control by the unsprung vibration suppression control unit 34 are performed.
  • comfort mode the control for giving priority to the unsprung vibration damping control by the unsprung vibration damping control unit 34 is performed while performing the frequency sensitive control by the frequency sensitive control unit 33b.
  • priority is given to driver input control by the driver input control unit 31, and control for adding the amount of unsprung vibration suppression control by the unsprung vibration control unit 34 to skyhook control by the skyhook control unit 33a is performed. To do.
  • the adjustment of the attenuation coefficient in each mode will be described.
  • FIG. 18 is a flowchart illustrating the attenuation coefficient arbitration process in the standard mode according to the first embodiment.
  • step S1 it is determined whether or not the S / A attitude damping coefficient k2 is larger than the unsprung damping damping coefficient k4. If larger, the process proceeds to step S4 and k2 is set as the damping coefficient.
  • step S2 a scalar amount ratio of the bull region is calculated based on the scalar amounts of the fur region, the leopard region, and the bull region described in the frequency response control unit 33b.
  • step S3 it is determined whether or not the ratio of the bull area is equal to or greater than a predetermined value.
  • the routine proceeds to step S5 and k4 is set.
  • FIG. 19 is a flowchart showing attenuation coefficient arbitration processing in the sport mode of the first embodiment.
  • step S11 the four-wheel damping force distribution ratio is calculated based on the four-wheel driver input damping coefficient k1 set by the driver input control.
  • the right front wheel driver input damping coefficient is k1fr
  • the left front wheel driver input damping coefficient is k1fl
  • the right rear wheel driver input damping coefficient is k1rr
  • the left rear wheel driver input damping coefficient is k1rl
  • xfl k1fl / (k1fr + k1fl + k1rr + k1rl)
  • xrr k1rr / (k1fr + k1fl + k1rr + k1rl)
  • xrl k1rl / (k1fr + k1fl + k1rr + k1rl)
  • xrl k
  • step S12 it is determined whether or not the damping force distribution ratio x is within a predetermined range (greater than ⁇ and smaller than ⁇ ). If it is within the predetermined range, it is determined that the distribution to each wheel is substantially equal, and the process proceeds to step S13. If any one is out of the predetermined range, the process proceeds to step S16. In step S13, it is determined whether or not the unsprung damping damping coefficient k4 is larger than the driver input damping coefficient k1. If it is determined that the unsprung damping damping coefficient k4 is larger, the process proceeds to step S15 and k4 is set as the first damping coefficient k. On the other hand, if it is determined that the unsprung damping damping coefficient k4 is equal to or less than the driver input damping coefficient k1, the process proceeds to step S14, and k1 is set as the first damping coefficient k.
  • step S16 it is determined whether or not the unsprung damping damping coefficient k4 is the maximum value max that S / A3 can be set. If it is determined that the maximum value is max, the process proceeds to step S17, and otherwise, the process proceeds to step S18. move on.
  • step S17 the maximum value of the four-wheel driver input damping coefficient k1 is the unsprung damping damping coefficient k4, and the damping coefficient that satisfies the damping force distribution ratio is calculated as the first damping coefficient k. In other words, a value that maximizes the damping coefficient while satisfying the damping force distribution rate is calculated.
  • step S18 a damping coefficient that satisfies the damping force distribution ratio in a range where all the four-wheel driver input damping coefficients k1 are equal to or greater than k4 is calculated as the first damping coefficient k.
  • a value that satisfies the damping force distribution ratio set by the driver input control and also satisfies the requirements of the unsprung vibration suppression control side is calculated.
  • step S19 it is determined whether or not the first attenuation coefficient k set in each of the above steps is smaller than the S / A attitude attenuation coefficient k2 set by skyhook control. Since the damping coefficient requested on the side is larger, the process proceeds to step S20 and k2 is set. On the other hand, if it is determined that k is equal to or greater than k2, the process proceeds to step S21 and k is set.
  • the damping force distribution rate required from the driver input control side is closely related to the vehicle body posture, and particularly because it is closely related to the driver's line-of-sight change due to the roll mode.
  • the highest priority is to secure the damping force distribution ratio.
  • the sky vehicle body posture can be maintained by selecting Skyhook control with select high.
  • FIG. 20 is a flowchart illustrating the attenuation coefficient arbitration process in the comfort mode according to the first embodiment.
  • step S30 it is determined whether or not the frequency sensitive damping coefficient k3 is larger than the unsprung damping damping coefficient k4. If it is determined that the frequency sensitive damping coefficient k3 is larger, the process proceeds to step S32 and the frequency sensitive damping coefficient k3 is set. On the other hand, if it is determined that the frequency sensitive damping coefficient k3 is equal to or less than the unsprung damping damping coefficient k4, the process proceeds to step S32 to set the unsprung damping damping coefficient k4.
  • the comfort mode priority is given to unsprung resonance control that basically suppresses unsprung resonance.
  • frequency sensitive control was performed as sprung mass damping control, and the optimum damping coefficient was set according to the road surface condition, so it was possible to achieve control that ensured riding comfort and lack of grounding feeling due to fluttering under the spring. Can be avoided by unsprung vibration suppression control.
  • the attenuation coefficient may be switched according to the bull ratio of the frequency scalar quantity. As a result, the ride comfort can be further ensured in the super comfort mode.
  • FIG. 21 is a flowchart illustrating the attenuation coefficient arbitration process in the highway mode according to the first embodiment. Since steps S11 to S18 are the same as the arbitration process in the sport mode, the description thereof is omitted.
  • step S40 the S / A attitude attenuation coefficient k2 by the skyhook control is added to the first attenuation coefficient k that has been adjusted up to step S18, and is output.
  • FIG. 22 is a time chart showing a change in attenuation coefficient when traveling on a wavy road surface and an uneven road surface.
  • the first damping coefficient k is always set as in the highway mode, a certain amount of damping force is always secured, and the vehicle body fluctuates even when the damping coefficient by the skyhook control is small. Such movement can be suppressed. Further, since it is not necessary to increase the skyhook control gain, it is possible to appropriately deal with road surface irregularities by using a normal control gain. In addition, since the skyhook control is performed with the first damping coefficient k set, unlike the damping coefficient limit, the damping coefficient decreasing process can be performed in the semi-active control region, and at the time of high-speed traveling It is possible to ensure a stable vehicle posture.
  • FIG. 23 is a flowchart illustrating a mode selection process based on the running state in the attenuation coefficient arbitration unit of the first embodiment.
  • step S50 it is determined whether or not the vehicle is in the straight traveling state based on the value of the steering angle sensor 7. If it is determined that the vehicle is traveling straight, the process proceeds to step S51. If it is determined that the vehicle is turning, the process proceeds to step S54. move on.
  • step S51 it is determined based on the value of the vehicle speed sensor 8 whether or not the vehicle speed is equal to or higher than a predetermined vehicle speed VSP1 representing a high vehicle speed state.
  • step S52 If it is determined that the vehicle speed is VSP1 or higher, the process proceeds to step S52 and the standard mode is selected. On the other hand, if it is determined that it is less than VSP1, the process proceeds to step S53 and the comfort mode is selected. In step S54, based on the value of the vehicle speed sensor 8, it is determined whether or not the vehicle speed is equal to or higher than a predetermined vehicle speed VSP1 representing a high vehicle speed state. On the other hand, if it is determined that it is less than VSP1, the process proceeds to step S56 to select the sport mode.
  • the standard mode when driving at a high vehicle speed in a straight running state, the standard mode is selected to stabilize the vehicle body posture by skyhook control and to suppress the high frequency vibration such as leopard and bull. In addition, unsprung resonance can be suppressed. Further, when traveling at a low vehicle speed, by selecting the comfort mode, it is possible to suppress unsprung resonance while suppressing the input of vibrations such as leopard and bull to the occupant as much as possible.
  • the highway mode is selected, so that it is controlled by the value obtained by adding the damping coefficient, so that basically a high damping force can be obtained.
  • the sport mode is selected, so that the vehicle posture during turning is positively secured by driver input control, and unsprung resonance is suppressed while skyhook control is performed as appropriate. Can travel in a stable vehicle posture.
  • the control example in which the driving state is detected and automatically switched is shown in the first embodiment.
  • a changeover switch that can be operated by the driver is provided to select the driving mode. You may control to. As a result, ride comfort and turning performance according to the driving intention of the driver can be obtained.
  • the sprung mass damping control units 101a and 33 or the skyhook control unit are used based on the wheel speed detected by the wheel speed sensor 5 in each traveling state estimation unit 100, 200, and 32.
  • the stroke speed, bounce rate, roll rate and pitch rate of each wheel used for the 201 skyhook control are estimated.
  • the stroke speed and the sprung state are estimated from the wheel speed, a scene is assumed in which the estimation accuracy decreases due to various factors. For example, when traveling on a low ⁇ road, a slip is likely to occur, and it is difficult to determine whether or not the wheel speed fluctuation accompanying the slip is due to road surface unevenness.
  • the wheel speed fluctuation amount due to changes in road surface unevenness and sprung state tends to be small, and it is difficult to distinguish from other noises.
  • the fluctuation of the braking / driving torque causes the wheel speed fluctuation, it is difficult to distinguish the fluctuation from the sprung state or the stroke speed.
  • the wheel speed fluctuates due to yaw rate or lateral acceleration in the non-linear region like the friction circle limit of the tire, making it difficult to distinguish from other noises.
  • the estimation accuracy is lowered, for example, a place to be increased as a damping force may be set low, and it becomes difficult to stabilize the sprung state.
  • the decrease in the estimated accuracy is merely a problem of accuracy, and it is not an abnormality such as a sensor failure or an actuator failure. Therefore, it can be said that it is desirable to continue the control within a possible range. Therefore, in the first embodiment, the estimated accuracy decrease detection unit 4a that detects when the estimated accuracy is reduced is provided, and when the estimated accuracy is reduced, at least performance equal to or higher than that of a general vehicle that does not perform vehicle system vibration control is ensured. However, by continuing the control as much as possible, it was decided to stabilize the sprung behavior accompanying the decrease in the estimation accuracy.
  • FIG. 24 is a control block diagram illustrating an estimated accuracy decrease detection process according to the first embodiment.
  • the estimated accuracy decrease detection unit 4a a plurality of accuracy decrease detection processes are executed based on various signals, and when the signal reception unit 400 detects accuracy decrease in any one of the processes, the accuracy decrease An accuracy decrease signal is output to the hold unit 401.
  • the accuracy decrease hold unit 401 continuously turns on the accuracy decrease flag while receiving the accuracy decrease signal and even if the accuracy decrease signal is interrupted for a predetermined time (1 second in the first embodiment). And Thereby, the control state based on the incorrect state estimation value is avoided while suppressing frequent switching of the accuracy decrease flag.
  • each accuracy fall detection process is demonstrated in order.
  • an anti-skid brake control unit (hereinafter referred to as an ABS control unit) that detects the slip state of each wheel during braking and performs pressure increase / decrease control so that the slip rate is a predetermined value or less. ),
  • a vehicle behavior control unit (hereinafter referred to as a VDC control unit) that controls the brake fluid pressure of a predetermined wheel so that the turning state (for example, yaw rate) of the vehicle becomes a target turning state, and when the vehicle starts.
  • a traction control unit (hereinafter referred to as a TCS control unit) that performs brake pressure increase control and engine torque down control in order to suppress drive slip.
  • the estimation accuracy may be lowered because the wheel speed fluctuation of each wheel is affected. Therefore, when the ABS flag, VDC flag, or TCS flag indicating that these controls are activated is turned on, a flag on signal is output to the brake control flag hold unit 410.
  • the brake control flag hold unit 410 outputs an estimated accuracy decrease signal while receiving the flag on signal.
  • the accuracy decrease signal is continuously output for a predetermined time (5 seconds in the first embodiment) set in advance from the falling edge of the flag-on signal. Thereby, even when the brake control flag is repeatedly turned on and off, the estimated accuracy lowering signal can be output stably.
  • the first to third traveling state estimation units 100, 200, and 32 are used to detect a component that varies with the stroke of S / A3 when estimating the stroke speed from the wheel speed data. Wheel speed is calculated. This is because the difference between the reference wheel speed and the wheel speed sensor value is extracted as a fluctuation component accompanying the stroke.
  • This reference wheel speed can ensure the accuracy of stroke speed estimation under the condition that no slip or the like occurs, but when slip occurs, it is possible to determine whether it is a fluctuation due to the stroke or a fluctuation in the wheel speed due to the slip. It becomes difficult.
  • a low-pass filter (0.5 Hz in the first embodiment) on the lower frequency side than the vibration frequency generated by the stroke speed, sprung speed, etc. is applied to the reference wheel speed, and the reference wheel speed after this low-pass filter action is the distance between the wheels. In the case where there is variation, the wheel speed is changed due to slip and it is detected that the estimated accuracy is lowered.
  • the reference wheel speed estimation unit 420 calculates the first wheel speed V0 that is the reference wheel speed of each wheel based on the vehicle body plan view model, as described in the reference wheel speed calculation unit of FIG.
  • the wheel speed sensor value detected by the wheel speed sensor 5 is ⁇ (rad / s)
  • the front wheel actual steering angle detected by the steering angle sensor 7 is ⁇ f (rad)
  • the rear wheel actual steering angle is ⁇ r (rad )
  • the vehicle body lateral speed is Vx
  • the yaw rate detected by the integrated sensor 6 is ⁇ (rad / s)
  • the vehicle speed estimated from the calculated reference wheel speed ⁇ 0 is V (m / s)
  • the reference to be calculated Wheel speed is VFL, VFR, VRL, VRR
  • front wheel tread is Tf
  • rear wheel tread is Tr
  • distance from vehicle center of gravity to front wheel is Lf
  • distance from vehicle center of gravity to rear wheel is Lr.
  • VFL (V-Tf / 2 ⁇ ⁇ ) cos ⁇ f + (Vx + Lf ⁇ ⁇ ) sin ⁇ f
  • VFR (V + Tf / 2 ⁇ ⁇ ) cos ⁇ f + (Vx + Lf ⁇ ⁇ ) sin ⁇ f
  • VRL (V ⁇ Tr / 2 ⁇ ⁇ ) cos ⁇ r + (Vx ⁇ Lr ⁇ ⁇ ) sin ⁇ r
  • VRR (V + Tr / 2 ⁇ ⁇ ) cos ⁇ r + (Vx-Lr ⁇ ⁇ ) sin ⁇ r
  • V is described as V0FL, V0FR, V0RL, V0RR (corresponding to the first wheel speed) as a value corresponding to each wheel.
  • V0FL ⁇ VFL-Lf ⁇ ⁇ sin ⁇ f ⁇ / cos ⁇ f + Tf / 2 ⁇ ⁇
  • V0FR ⁇ VFR-Lf ⁇ ⁇ sin ⁇ f ⁇ / cos ⁇ f-Tf / 2 ⁇ ⁇
  • V0RL ⁇ VRL + Lr ⁇ ⁇ sin ⁇ r ⁇ / cos ⁇ r + Tr / 2 ⁇ ⁇
  • V0RR ⁇ VRR + Lf ⁇ ⁇ sin ⁇ f ⁇ / cos ⁇ r-Tr / 2 ⁇ ⁇
  • the difference determination unit 422 calculates the following values, respectively.
  • df3 VOFL-VORL
  • df4 VOFR ⁇ VORR ⁇ Warp component (diagonal difference)
  • the reference wheel speed hold unit 423 continuously outputs the accuracy decrease signal while receiving the estimated accuracy decrease signal and until a predetermined time (2 seconds in the first embodiment) elapses from the end of reception. Thereby, even when the difference determination unit 422 repeatedly turns on and off the estimated accuracy decrease signal, the estimated accuracy decrease signal can be stably output.
  • a plan view model is set to estimate the lateral acceleration Yg.
  • Yg (VSP 2 / (1 + A ⁇ VSP 2 )) ⁇ ⁇ f
  • A is a predetermined value.
  • the roll rate is estimated from the lateral acceleration Yg estimated based on this relationship. At this time, in a situation where the estimation accuracy of the stroke speed is lowered due to the occurrence of slip or the like, the estimated value of the lateral acceleration deviates from the actual value.
  • a low-pass filter (0.5 Hz in the first embodiment) on the lower frequency side than the vibration frequency generated by the stroke speed, sprung speed, etc. is applied to the estimated lateral acceleration, and the lateral acceleration after this low-pass filter action is the lateral acceleration.
  • the estimated estimated lateral acceleration and estimated yaw rate and the sensor value detected by the integrated sensor 6 are converted into a region on the lower frequency side than the frequency region including the stroke speed and the sprung speed. Filter with a 0.5 Hz low-pass filter to extract the stationary component. Then, the difference determination unit 432 calculates the difference between the estimated value and the sensor value.
  • the output of the estimated accuracy lowering signal is stopped when the predetermined value dfthi is equal to or less than a value obtained by multiplying 0.8.
  • the plan view model hold unit 433 continuously outputs the accuracy decrease signal while receiving the estimated accuracy decrease signal and until a predetermined time (2 seconds in the first embodiment) elapses from the end of reception. Thereby, even when the difference determination unit 432 repeatedly turns on and off the estimated accuracy decrease signal, the estimated accuracy decrease signal can be stably output.
  • shift determination unit 440 when the shift signal indicates a reverse range or a parking range, an accuracy decrease signal is continuously output to shift hold unit 441.
  • the shift hold unit 441 continuously outputs an accuracy decrease signal until a predetermined time (1 second in the first embodiment) elapses from the end of reception of the estimated accuracy decrease signal from the viewpoint of preventing hunting associated with the shift operation. To do.
  • the braking force release determination unit 450 determines whether or not the brake switch has been switched from on to off, and outputs an accuracy decrease signal to the brake switch hold unit 451 when it is determined that the switch has been switched.
  • the brake switch hold unit 451 continuously outputs an accuracy decrease signal until a predetermined time (1 second in the first embodiment) elapses from the time when the brake switch is switched off.
  • Tw Te ⁇ R TRQCVT ⁇ R AT ⁇ R FINAL ⁇ ⁇ TOTAL
  • Tw is the wheel end drive torque
  • Te is the engine torque
  • R TRQCVT is the torque converter torque ratio
  • R AT is the gear ratio of the automatic transmission
  • R FINAL is the final gear ratio
  • ⁇ TOTAL is the drive system efficiency.
  • the wheel end braking torque varies during braking.
  • the braking force is proportional to the wheel cylinder pressure (substantially the master cylinder pressure during normal braking when ABS or other control is not performed). The power is estimated.
  • the low-pass filter 460 determines the wheel end driving torque in a lower frequency region than the frequency region including the stroke speed and sprung speed. Filter with a certain 0.5Hz low-pass filter to extract the stationary components. Then, the change rate of the wheel end driving torque is calculated by differentiation in the pseudo-differentiating unit 461. Then, the change rate determination unit 462 outputs an estimated accuracy lowering signal to the wheel end drive torque hold unit 463 when the calculated wheel end drive torque change rate is equal to or greater than a predetermined value dfthi set in advance.
  • the output of the estimated accuracy lowering signal is stopped when the predetermined value dfthi is equal to or less than a value obtained by multiplying 0.8.
  • the wheel end drive torque hold unit 463 continuously outputs the accuracy decrease signal while receiving the estimated accuracy decrease signal and until a predetermined time (1 second in the case of the first embodiment) elapses from the end of reception. .
  • the rate-of-change determination unit 462 repeatedly turns on and off the estimated accuracy decrease signal, the estimated accuracy decrease signal can be stably output.
  • each detection process is performed, and when any of these detects a decrease in accuracy, the estimated accuracy decrease flag is turned on, and an appropriate control process is executed when the accuracy decreases.
  • the control process at the time of estimation accuracy fall is demonstrated.
  • the estimated accuracy decrease detection control unit 5a When the estimated accuracy decrease flag is turned on, that is, when the estimated accuracy decrease of the stroke speed is detected, the estimated accuracy decrease detection control unit 5a outputs the engine attitude control amount as zero to the engine control unit 102. . Further, when the estimated accuracy decrease detection unit 5a is turned on, the estimated accuracy decrease detection control unit 5a outputs the brake attitude control amount to zero to the brake control unit 202. At this time, the brake control unit 202 gradually decreases the brake posture control amount so that the brake posture control amount smoothly decreases to zero over a certain transition time (for example, 1 second).
  • the sprung mass damping control by the engine 1 and the brake 20 is stopped while a decrease in the estimated accuracy of the stroke speed is detected.
  • the stroke speed is estimated from the fluctuation in the predetermined frequency region of the wheel speed, and the sprung behavior control using the engine 1 and the brake 20 is performed according to the stroke speed, so the estimated accuracy of the stroke speed is reduced.
  • the sprung behavior may be disturbed due to deterioration of controllability. Therefore, in this case, by stopping the sprung mass damping control by the engine 1 and the brake 20, it is possible to suppress the disturbance of the vehicle body posture due to the decrease in the estimated accuracy, and to maintain a stable vehicle body posture.
  • FIG. 25 is a control block diagram illustrating the configuration of the estimation accuracy decrease detection control unit 5a according to the first embodiment.
  • the estimated accuracy decrease flag, the vehicle speed VSP detected by the vehicle speed sensor 8, and the value of the vehicle speed VSP before one sampling period (one clock) are input.
  • the vehicle speed calculation unit 501 outputs the vehicle speed VSP detected by the vehicle speed sensor 8 to the delay element 502 when the estimated accuracy decrease flag is turned off.
  • the flag is turned off.
  • the vehicle speed immediately before one sampling period that is, the vehicle speed immediately before the decrease in the estimation accuracy of the stroke speed is detected is output to the attenuation coefficient setting unit 503.
  • the delay element 502 delays a signal for one clock.
  • the attenuation coefficient setting unit 503 inputs the vehicle speed immediately before the decrease in the estimated accuracy of the stroke speed, the outside air temperature detected by the temperature sensor 14, and the current control mode are input, and the attenuation coefficient k5 when the estimated accuracy decreases. Is output. A method for setting the attenuation coefficient k5 will be described later.
  • the damping force control amount computing unit 504 computes a control signal for S / A3 based on the damping coefficient k5 and a predetermined virtual stroke speed.
  • the virtual stroke speed is a fixed value
  • FIG. 26 is an explanatory diagram illustrating a method for setting the attenuation coefficient when the estimated accuracy is reduced in the attenuation coefficient setting unit according to the first embodiment.
  • the damping coefficient k5 is basically a value proportional to the vehicle speed (the vehicle speed immediately before the drop in estimated accuracy of the stroke speed is detected), and the damping coefficient of the front wheel side Fr is the same as the damping coefficient of the rear wheel side Rr at the same vehicle speed. The characteristics should be higher.
  • the attenuation coefficient k5 is a value corresponding to the control mode. Specifically, the highest value is set in the sport mode and the highway mode, and the lowest value is set in the comfort mode. In the standard mode, an intermediate value between the sports mode (highway mode) and the comfort mode is set.
  • the attenuation coefficient k5 in the sport mode and the highway mode is an attenuation coefficient that provides an upper limit damping force control amount that does not transmit vibration in the leopard region (3 to 6 Hz) to the occupant.
  • the damping coefficient setting unit 503 includes a friction circle estimation unit 503a, and the friction circle estimation unit 503a estimates whether or not the size of the friction circle of each tire is a predetermined value or less based on the outside air temperature. When the outside air temperature is within a predetermined range (for example, 5 ° C. ⁇ outside air temperature ⁇ 30 ° C.), the friction circle estimating unit 503a estimates that the size of the friction circle of each tire is larger than the predetermined value, and the predetermined range.
  • a predetermined range for example, 5 ° C. ⁇ outside air temperature ⁇ 30 ° C.
  • the damping coefficient setting unit 503 is the damping coefficient when it is estimated that the size of the friction circle of each tire is equal to or less than a predetermined value while traveling in the comfort mode, and the damping coefficient when it is estimated that the tire is larger than the predetermined value. Higher value (same attenuation coefficient as standard mode).
  • vehicle speed sensitive control is performed in which the damping force of S / A3 is a fixed damping force according to the control mode.
  • the damping force of S / A3 is a fixed damping force according to the control mode.
  • the fixed damping force is determined from the vehicle speed immediately before the estimated accuracy drop is detected, and it does not depend on the stroke speed, which is highly likely to be erroneously estimated. Due to the transition to the stable control state, it is possible to suppress both the steering stability and the decrease in ride comfort and the instability of the vehicle behavior.
  • the damping coefficient k5 is set from the vehicle speed immediately before the estimated accuracy decrease is detected, and the fixed damping force is determined based on the damping coefficient k5 and a predetermined virtual stroke speed (0.1 m / s). At this time, the damping coefficient k5 is set to a higher value as the vehicle speed immediately before the estimated accuracy decrease is detected, so that an optimum damping force that matches the vehicle speed is obtained. That is, it is possible to achieve both of ensuring the riding comfort in the low vehicle speed range and ensuring the steering stability in the high vehicle speed range.
  • the damping coefficient k5 is set to a higher value in the order of the sport mode, the highway mode, the standard mode, and the comfort mode, a fixed damping force that matches the control mode can be set.
  • the damping force is increased to give priority to steering stability
  • in comfort mode the damping force is reduced to give priority to riding comfort
  • in standard mode steering stability and riding comfort are set with damping force in the middle.
  • the fixed damping force of the front wheels is made larger than the fixed damping force of the rear wheels, so the nose dive can be suppressed and the steer tendency can be changed to an understeer tendency, which improves the stability of turning behavior. It can be secured.
  • the outside air The fixed damping force is made larger than when the temperature is outside the predetermined range (outside air temperature ⁇ 5 ° C. or outside air temperature ⁇ 30 ° C.). In other words, the fixed damping force is increased when the low ⁇ state occurs during traveling in the comfort mode than when the high ⁇ state.
  • the outside air temperature is 5 ° C. or lower, road surface freezing is predicted, and therefore there is a high possibility of being in a low ⁇ state.
  • the outside air temperature is 30 ° C. or higher, the grip performance is deteriorated particularly in the studless tire, and therefore, there is a high possibility of being in a low ⁇ state.
  • reverse steer means that the steering tendency changes from an understeer tendency to an oversteer tendency during turning. Therefore, in the first embodiment, in the comfort mode, the fixed damping force in the low ⁇ state is set larger than the fixed damping force in the high ⁇ state. As a result, it is possible to suppress a reduction in the ground contact load of the rear tire and to suppress the generation of a nose dive. Therefore, it is possible to prevent the steering tendency from becoming an oversteer tendency and to ensure the stability of the turning behavior.
  • the fixed damping force in the low ⁇ state is set to the same value as the fixed damping force in the high ⁇ state. This is because the above three control modes have a larger fixed damping force than the comfort mode, and therefore it is unlikely that the tire grip force will exceed the limit value when turning even in a low ⁇ state. Also, in sport mode and highway mode, the fixed damping force is the maximum fixed damping force that does not transmit vibrations that move to the occupants, thus improving steering stability while suppressing deterioration in riding comfort. Can do.
  • the low ⁇ state is excluded as a condition for determining a decrease in the estimated accuracy of the stroke speed.
  • the vehicle behavior is less likely to be unstable even in low ⁇ conditions. This is because it is desirable to continue excellent normal control (sprung posture control, driver input control, and unsprung vibration suppression control).
  • the low ⁇ state is determined from the outside air temperature, if it is determined that the estimated accuracy is reduced when the low ⁇ state is present, the outside air temperature is predetermined even during steady running. When the temperature is out of the range (outside air temperature ⁇ 5 ° C. or outside air temperature ⁇ 30 ° C.), the vehicle speed control is always shifted.
  • the command current value (command current value at the time of estimation accuracy decrease) is output from the control unit 5a when the estimated accuracy decrease is detected
  • the attenuation adjusted by the attenuation coefficient arbitration unit 35b instead of the command current value (normal command current value) based on the coefficient and the stroke speed
  • the command current value when the estimated accuracy is reduced is output to S / A3.
  • the command current value is gradually changed so that the command current value smoothly transitions from the current command current value over the predetermined transition time to the command current value when the estimated accuracy decreases.
  • the transition time is set to a time of at least a period (for example, 0.5 Hz) equal to or less than the sprung resonance (1.2 Hz), for example, 1 second.
  • Example 1 has the following effects. (1) A wheel speed sensor 5 that detects the wheel speed of each wheel, and a stroke speed calculation unit 321 (stroke speed estimation means) that estimates the stroke speed of the S / A 3 based on the sensor value detected by the wheel speed sensor 5 And an S / A controller 3a (damping force control means) that calculates a damping force control amount of S / A3 based on the stroke speed estimated by the stroke speed calculating unit 321 and outputs the S / A3 damping force to the S / A3.
  • stroke speed calculation unit 321 stroke speed estimation means
  • S / A controller 3a dampping force control means
  • the estimated accuracy decrease detection unit 4a (estimated accuracy decrease detection means) that detects a decrease in estimated accuracy of the stroke speed estimated by the stroke speed calculation unit 321 and the estimated accuracy decrease detection unit 4a decrease the estimation accuracy. Is detected, the damping force control amount corresponding to the vehicle speed is calculated and output to the S / A 3. And a friction circle estimator 503a (friction circle estimator) for estimating the size of the friction circle of the tire of each wheel, and the estimated accuracy decrease detection control unit 5a performs friction by the friction circle estimator 503a.
  • the damping force control amount when it is estimated that the size of the circle is equal to or less than the predetermined value is made larger than the damping force control amount when it is estimated that the circle is larger than the predetermined value.
  • the estimated accuracy decrease detection control unit 5a calculates a damping force control amount according to the vehicle speed immediately before the estimated accuracy decrease of the stroke speed is detected. Thereby, a damping force control amount that matches the actual vehicle speed can be set.
  • the S / A controller 3a calculates a damping force control amount according to the current control mode, and the estimated accuracy decrease detection control unit 5a is the control mode in which the upper limit of the damping force control range with respect to the stroke speed is the smallest.
  • the damping force control amount when the size of the friction circle is estimated to be a predetermined value or less by the friction circle estimation unit 503a Is set to be larger than the damping force control amount when it is estimated to be larger than the predetermined value.
  • the estimated accuracy decrease detection control unit 5a makes the front wheel damping force control amount larger than the rear wheel damping force control amount. Therefore, since nose dive can be suppressed, the steering tendency becomes an understeer tendency, and the stability of the turning behavior can be secured.
  • the estimated accuracy decrease detection time control unit 5a gradually multiplies a predetermined transition time (1 second) from the damping force control amount immediately before the estimated accuracy decrease is detected to the damping force control amount when the estimated accuracy decreases. Change. Thereby, it can suppress that the damping force of S / A3 changes suddenly and a vehicle body attitude
  • the estimated accuracy decrease detection control unit 5a sets the predetermined transition time as a time that is a frequency equal to or lower than the sprung resonance frequency. As a result, the vibration transmission characteristic more than the sprung resonance is reduced, the high frequency vibration is suppressed, and a smooth riding comfort is obtained.
  • the temperature sensor 14 (outside air temperature detecting means) for detecting the outside air temperature is provided, and the friction circle estimation unit 503a determines the size of the friction circle of the tire of each wheel based on the outside air temperature detected by the temperature sensor 14. It is estimated whether it is below a predetermined value.
  • the size of the friction circle of the tire changes depending on the friction coefficient ⁇ between the tire and the road surface, and the friction coefficient ⁇ can be predicted to some extent by the outside air temperature. It can be easily and quickly estimated whether or not there is any complicated calculation.
  • a wheel speed sensor 5 that detects the wheel speed of each wheel, and if no decrease in the estimated accuracy of the S / A3 stroke speed estimated from the wheel speed is detected, S is determined based on the stroke speed.
  • / A3 damping force control amount is calculated, and when a decrease in estimated accuracy is detected, the damping force control amount is calculated according to the vehicle speed and the size of the wheel friction circle is equal to or less than a predetermined value.
  • an S / A controller 3a (controller) that makes the damping force control amount according to the vehicle speed larger than the damping force control amount according to the vehicle speed when the vehicle speed is larger than a predetermined value.
  • the unstable control state depending on the stroke speed can be shifted to a more stable control state, and the stabilization of the vehicle body posture can be achieved.
  • the friction circle of the wheel is small, by increasing the damping force control amount than when it is large, it is possible to improve both the ground contact property in the low ⁇ state and the riding comfort in the high ⁇ state.
  • (9) It has a wheel speed sensor 5 (sensor) for detecting the wheel speed, and the S / A controller 3a (controller) has not detected a decrease in the estimation accuracy of the S / A3 stroke speed estimated from the wheel speed.
  • the S / A3 damping force control amount is calculated based on the stroke speed.
  • the damping force control amount corresponding to the vehicle speed is calculated and the friction circle of the wheel is calculated.
  • the damping force control amount corresponding to the vehicle speed when the magnitude is equal to or less than the predetermined value is set larger than the damping force control amount corresponding to the vehicle speed when the magnitude is larger than the predetermined value.
  • the unstable control state depending on the stroke speed can be shifted to a more stable control state, and the stabilization of the vehicle body posture can be achieved.
  • the friction circle of the wheel is small, by increasing the damping force control amount than when it is large, it is possible to improve both the ground contact property in the low ⁇ state and the riding comfort in the high ⁇ state.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)

Abstract

L'invention vise à proposer un dispositif de commande et un procédé de commande pour un véhicule qui peuvent garantir la sécurité dans le comportement au moment de tourner même dans le cas d'une faible précision dans l'estimation de la vitesse de déplacement dans un état µ faible. A cet effet, selon l'invention, la quantité de commande de force d'amortissement d'un absorbeur de chocs à force d'amortissement variable est calculée sur la base de la vitesse de déplacement lorsqu'aucune diminution n'est détectée dans la précision d'estimation de la vitesse de déplacement de l'absorbeur de chocs à force d'amortissement variable estimée à partir de la vitesse de roue de véhicule, la quantité de commande de force d'amortissement correspondant à la vitesse de véhicule étant calculée lorsqu'une diminution de la précision d'estimation est détectée, et la quantité de commande de force d'amortissement correspondant à la vitesse de véhicule lorsque la dimension du cercle de frottement des roues de véhicule est une valeur prédéterminée ou moins étant accrue au-dessus de la quantité de commande de force d'amortissement correspondant à la vitesse de véhicule lorsque le cercle de frottement est supérieur à la valeur prédéterminée.
PCT/JP2013/060587 2012-06-06 2013-04-08 Dispositif de commande de véhicule et procédé de commande de véhicule WO2013183349A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012-128488 2012-06-06
JP2012128488A JP2015164816A (ja) 2012-06-06 2012-06-06 車両の制御装置及び車両の制御方法

Publications (1)

Publication Number Publication Date
WO2013183349A1 true WO2013183349A1 (fr) 2013-12-12

Family

ID=49711750

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2013/060587 WO2013183349A1 (fr) 2012-06-06 2013-04-08 Dispositif de commande de véhicule et procédé de commande de véhicule

Country Status (2)

Country Link
JP (1) JP2015164816A (fr)
WO (1) WO2013183349A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3100878A3 (fr) * 2015-03-19 2017-08-09 Honda Motor Co., Ltd. Appareil de commande de suspension pour véhicule
EP3100879A3 (fr) * 2015-03-19 2017-08-09 Honda Motor Co., Ltd. Dispositif de commande de suspension pour véhicule
CN110023166A (zh) * 2016-12-09 2019-07-16 日立汽车系统株式会社 车辆运动状态推断装置

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS632604U (fr) * 1986-06-24 1988-01-09
JP2006335229A (ja) * 2005-06-02 2006-12-14 Toyota Motor Corp スプリット路面上での車輪の駆動滑りを抑制する車輌
JP2009083614A (ja) * 2007-09-28 2009-04-23 Hitachi Ltd サスペンション制御装置
JP2009255777A (ja) * 2008-04-17 2009-11-05 Yamaha Motor Co Ltd 懸架装置の制御装置および車両
WO2010106137A1 (fr) * 2009-03-19 2010-09-23 Societe De Technologie Michelin Procédé de détermination d'un coefficient d'adhérence d'une roue par mise en pince simultanée
JP2011173465A (ja) * 2010-02-23 2011-09-08 Honda Motor Co Ltd 減衰力可変ダンパの制御装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS632604U (fr) * 1986-06-24 1988-01-09
JP2006335229A (ja) * 2005-06-02 2006-12-14 Toyota Motor Corp スプリット路面上での車輪の駆動滑りを抑制する車輌
JP2009083614A (ja) * 2007-09-28 2009-04-23 Hitachi Ltd サスペンション制御装置
JP2009255777A (ja) * 2008-04-17 2009-11-05 Yamaha Motor Co Ltd 懸架装置の制御装置および車両
WO2010106137A1 (fr) * 2009-03-19 2010-09-23 Societe De Technologie Michelin Procédé de détermination d'un coefficient d'adhérence d'une roue par mise en pince simultanée
JP2011173465A (ja) * 2010-02-23 2011-09-08 Honda Motor Co Ltd 減衰力可変ダンパの制御装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3100878A3 (fr) * 2015-03-19 2017-08-09 Honda Motor Co., Ltd. Appareil de commande de suspension pour véhicule
EP3100879A3 (fr) * 2015-03-19 2017-08-09 Honda Motor Co., Ltd. Dispositif de commande de suspension pour véhicule
CN110023166A (zh) * 2016-12-09 2019-07-16 日立汽车系统株式会社 车辆运动状态推断装置
CN110023166B (zh) * 2016-12-09 2022-08-02 日立安斯泰莫株式会社 车辆运动状态推断装置

Also Published As

Publication number Publication date
JP2015164816A (ja) 2015-09-17

Similar Documents

Publication Publication Date Title
JP5900613B2 (ja) 車両の制御装置及び車両の制御方法
JP5807717B2 (ja) 車両の制御装置及び車両の制御方法
JP5751385B2 (ja) 車両の制御装置及び車両の制御方法
JP5733431B2 (ja) 車両の制御装置及び車両の制御方法
JP5741719B2 (ja) 車両の制御装置及び車両の制御方法
JP5741718B2 (ja) 車両の制御装置及び車両の制御方法
JP5733430B2 (ja) 車両の制御装置及び車両の制御方法
WO2013100121A1 (fr) Dispositif de commande de véhicule
WO2013111743A1 (fr) Système et procédé de commande de véhicule
WO2013133059A1 (fr) Appareil de commande de véhicule, et procédé de commande de véhicule
WO2013183349A1 (fr) Dispositif de commande de véhicule et procédé de commande de véhicule
JP5811277B2 (ja) 車両の制御装置及び車両の制御方法
WO2013172123A1 (fr) Dispositif de commande de véhicule et procédé de commande de véhicule
WO2013115169A1 (fr) Dispositif de commande pour véhicule et procédé de commande pour véhicule
JP5737433B2 (ja) 車両の制御装置
JP5970831B2 (ja) ピッチレイト推定装置
WO2013111742A1 (fr) Système et procédé de commande de véhicule
JP5807684B2 (ja) 車両の制御装置及び車両の制御方法
JP5862685B2 (ja) 車両の制御装置及び車両の制御方法
JP5929923B2 (ja) 車両の制御装置及び車両の制御方法
JP2013151249A (ja) ロールレイト推定装置
WO2013161637A1 (fr) Dispositif de commande de véhicule et procédé de commande de véhicule
WO2013115007A1 (fr) Dispositif de commande de véhicule
WO2013111741A1 (fr) Système et procédé de commande de véhicule
WO2013111733A1 (fr) Système et procédé de commande de véhicule

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 13800091

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 13800091

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP