SUSPENSION SYSTEM

Abstract

A suspension system S according to the present invention is configured to control actuators AFR, AFL, ARR, ARL by determining a pitch damping force FP and a roll damping force FR to cancel roll and pitch moments MP, MR of a body B, and determining target control forces FTFR, FTFL, FTRR, FTRL in consideration of the pitch damping force FP and the roll damping force FR. When the pitch damping force FP and the roll damping force FR are output to the actuators AFR, AFL, ARR, ARL, the actuators AFR, AFL, ARR, ARL can each generate a control force for cancelling a force acting on the body B not later but preliminarily.

Description

TECHNICAL FIELD

The present invention relates to a suspension system.

BACKGROUND ART

Such a suspension system as disclosed in JPH03070616 W or JPH03070617 W includes four fluid pressure cylinders interposed between a body of a vehicle and four front and rear, right and left wheels of the vehicle, and a controller for controlling the fluid pressure cylinders.

The controller includes four vertical acceleration sensors for detecting vertical accelerations immediately above the fluid pressure cylinders of the body, and calculates a roll rate or a pitch rate on the basis of the four vertical accelerations.

Furthermore, the controller is configured to calculate a command value for damping rolling or pitching motion on the basis of the roll rate or the pitch rate for each of the four fluid pressure cylinders to control the fluid pressure cylinders.

Specifically, the controller multiplies the roll rate by a gain to cause each fluid pressure cylinder to generate a force proportional to the roll rate or multiplies the pitch rate by a gain to cause each fluid pressure cylinder to generate a force proportional to the pitch rate, damping rolling or pitching motion.

SUMMARY OF THE INVENTION

Thus, in a conventional suspension system, when a body of a running vehicle rolls and pitches due to vibration input from a road surface, fluid pressure cylinders are caused to generate a force damping the rolling or pitching motion to damp the rolling or pitching motion of the body.

However, since input to the body due to wheel vibration is not taken into consideration, rolling or pitching motion of the body cannot be fully damped, and the body has been required to have an improved vibration damping effect.

Therefore, the present invention has bees made to solve the above problems, and an object of the present invention is to provide a suspension system which can provide an improved vibration damping effect for a body of a vehicle.

For this reason, the suspension system according to the present invention is configured to control an actuator by determining a pitch damping force and a roll damping force to cancel the roll moment and pitch moment of the body, respectively, and determining a target control force in consideration of the pitch damping force and the roll damping force.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a diagram illustrating a configuration of a suspension system according to the present invention.

FIG. 2 is a diagram illustrating an exemplary configuration of an actuator.

FIG. 3 is a diagram illustrating the center of gravity, the wheelbase, and the tread of a vehicle.

FIG. 4 is a diagram illustrating a balanced state between a moment according to a pitch damping force and a roll damping force, a pitch moment, and a roll moment.

FIG. 5 is a diagram illustrating an exemplary configuration of a road input reduction control calculation unit.

FIG. 6 is a diagram illustrating another variation of the suspension system.

DESCRIPTION OF EMBODIMENTS

Hereinafter, the present invention will be described on the basis of embodiments with reference to the drawings. As illustrated in FIG. 1, a suspension system S includes four actuators A_FR, A_FL, A_RR, and A_RL interposed between a body B of a vehicle V and four front and rear, right and left wheels W_FR, W_FL, W_RR, and W_RL of the vehicle V, and a controller C for controlling the actuators A_FR, A_FL, A_RR, and A_RL.

As illustrated in FIG. 2, the actuators A_FR, A_FL, A_RR, and A_RL each includes an extensible cylinder device AC, a pump 4, and a hydraulic circuit FC provided between the cylinder device AC and the pump 4 to supply a fluid discharged from the pump 4 to the cylinder device AC to extend and contract the cylinder device AC.

In this suspension system S, the cylinder device AC includes a cylinder 1, a piston. 2 movably inserted into the cylinder 1 to partition the cylinder 1 into an extension chamber R1 and an compression chamber R2, and a rod 3 movably inserted into the cylinder 1 to be connected to the piston 2. The rod 3 passes through only the extension chamber R1, and the cylinder device AC is a so-called single rod cylinder device. Note that a reservoir. R is provided independent of the cylinder device AC, in FIG. 2, but, without detailed illustration, an outer cylinder may be provided to be disposed on the outer peripheral side of the cylinder 1 in the cylinder device AC to form an annular gap as the reservoir R between the cylinder 1 and the outer cylinder.

The cylinder device AC is interposed between the body B and each of the wheels W_FR, W_FL, W_RR, and W_RL, by connecting the cylinder 1 to one of the body B of the vehicle V and each of the wheels W_FR, N_FL, W_RR and W_RL and connecting the rod 3 to the other of the body B and each of the wheels W_FR, W_FL, W_RR, and W_RL. Note that between the body B and each of the wheels W_FR, W_FL, W_RR, and W_IL, a suspension spring Sp is interposed in parallel to the cylinder device AC.

Then, the fluid, such as hydraulic oil, is filled in the extension chamber R1 and the compression chamber R2, and the fluid is accumulated in the reservoir R. The fluid is also filled in the reservoir R and a gas spring, a spring, or both of the springs press the filled fluid. For the fluid filled in the extension chamber R1, the compression chamber R2, the reservoir R, and the reservoir R, a fluid, such as water or aqueous solution, may be employed in addition to the hydraulic oil. Furthermore, in the present invention, a chamber compressed during an extension process is defined as the extension chamber R1, and a chamber compressed during a contraction process is defined as the compression chamber R2.

The pump 4 has a suction side from which the fluid is sucked and a discharge side from which the fluid is discharged for unidirectional discharge of the fluid, and the pump is driven by a motor 13. The motor 13 may employ various types of motors, such as a brushless motor, an induction motor, or a synchronous motor, regardless of direct current or alternate current.

The suction side of the pump 4 is connected to the reservoir R through the pump passage 14, and the discharge side is connected to the hydraulic circuit FC. Accordingly, the pump 4 driven by the motor 13 sucks the fluid from the reservoir R. and discharges the fluid to the hydraulic circuit PC.

Furthermore, the motor 13 for driving the pump 4 is controlled by the controller C. The controller C can adjust the amount of current to be supplied to the motor 13, and can control the rotation rate of the pump 4, in addition to driving and stopping the pump 4. That is, the pump 4 is driven and controlled by the controller C.

The hydraulic circuit PC includes an electromagnetic valve controlled by the controller C, and the fluid discharged from the pump 4 can be supplied to the extension chamber R1 and the compression chamber R2 in the cylinder device AC. Furthermore, the hydraulic circuit PC discharges the rest of the fluid discharged from any of the extension chamber R1 and the compression chamber R2 and the rest of the fluid discharged from the pump 4 to the reservoir R. In addition, in accordance with a command from the controller C, the hydraulic circuit PC adjusts the extension chamber R1 and the compression chamber R2 in pressure to control the thrust of the cylinder device AC, causing the cylinder device AC to function as active suspension. As described above, the controller C can control the thrust in each of the actuators A_FR, A_FL, A_RR, and A_RL in accordance with a target control force obtained by the controller C itself.

As illustrated in FIG. 1, the controller C includes three acceleration sensors 21, 22, and 23, as acceleration sensor 24, an acceleration sensor 25, acceleration sensors 26, 27, 28, and 29, a body control calculation unit 30, a road input reduction control calculation unit 31, a target control force calculation unit 32, and a driver 33. The three acceleration sensors 21, 22, and 23 are installed in the body B to detect vertical accelerations G₁, G₂, and G₃, respectively, the acceleration sensor 24 is installed in the body B to detect a lateral acceleration. G_lat of the body B, the acceleration sensor 25 is installed in the body B to detect a longitudinal acceleration G_long of the body B, the acceleration sensors 26, 27, 28, and 29 detect vertical accelerations G_UFR, G_UFL, G_URR, and G_URL of the four wheels W_FR, W_RL, W_RR, and W_RL, respectively, and the driver 33 drives the motor 13, and the electromagnetic valve in the hydraulic circuit FC.

The acceleration sensors 21, 22, and 23 detect the vertical accelerations G₁, G₂, and G₃ in a vertical direction of the body B, and are installed at any three non-collinear points is the longitudinal direction or lateral direction of the body B. The acceleration sensors 21, 22, and 23 output the detected vertical accelerations G₁, G₂ and G₃ to the body control calculation unit 30. The acceleration sensor 24 and the acceleration sensor 25 input the detected lateral acceleration G_lat and longitudinal acceleration G_long, to the body control calculation unit 30. The acceleration sensors 26, 27, 28, and 29 input the detected vertical accelerations G_UFR, G_UFL, G_URR, and G_URL respectively to the road input reduction control calculation unit 31.

The body control calculation unit 30 includes a speed calculation unit 30a and a control force calculation unit 30b. The speed calculation unit 30a processes the accelerations G₁, G₂, and G₃ to determine a bounce rate V_B, a pitch rate V_P, and a roll rate V_R of the body B, and the control force calculation unit 30b determines body control forces F_FR, F_RR, and F_RL to be generated by the four actuators A_FR, A_FL, A_RR, and A_RL, on the basis of the bounce rate V_B, the pitch rate V_P, the roll rate V_R, the lateral acceleration G_lat, and the longitudinal acceleration G_long determined by the speed calculation unit 30a.

The speed calculation unit 30a firstly integrates the accelerations G₁, G₂, and G₃ to determine three vertical rates. When obtaining vertical rates at any three non-collinear points in the longitudinal direction or lateral direction of the body B, considering the body B as a rigid body, the rates of vertical, longitudinal, and lateral rotations of the body B can be obtained. Thus, on the basis of these rates, the speed calculation unit 30a determines the bounce rate V_B as a vertical rate at the position of the center of gravity of the body B, the pitch rate V_P as an angular rate of rotation in the front-back direction at the position of the center of gravity, and an angular rate of rotation in the lateral direction at the center of gravity and the roll rate V_R.

The control force calculation unit 30b receives the input of the bounce rate V_B, the pitch rate V_P, and the roll rate V_F, determined by the speed calculation unit 30a, and the lateral acceleration G_lat and the longitudinal acceleration. G_long detected by the acceleration sensor 24 and the acceleration sensor 25. Then, the control force calculation unit 30b determines the body control forces F_FR, F_FL, F_RR, and F_RL, on the basis of the bounce rate V_B, the pitch rate V_P, the roll rate V_R, the lateral acceleration. G_lat, and the longitudinal acceleration G_long.

As illustrated in FIG. 3, a longitudinal distance from the center of gravity to the front wheels W_FR and W_FL is designated L_F, a longitudinal distance from the center of gravity to the rear wheels W_RR and W_RL is designated L_R, and tread between the right wheel W_FR (W_RR) and the left wheel W_FL (W_RL) is designated W. The control force calculation unit 30b multiplies the bounce rate V_B by a gain to determine a control force for damping the vertical vibration of the body B.

Furthermore, the control force calculation unit 30b multiplies the pitch rate V_P by the gain to determine a damping moment in a pitch direction, and divides the damping moment by wheelbase (L_F+L_R) to determine a control force for damping the vibration of the body B due to pitching.

Furthermore, the control force calculation unit 30b multiplies the roll rate V_R by the gain to determine a damping moment in a roll direction, and divides the damping moment by tread W to determine a control force for damping the vibration of the body B due to rolling.

Furthermore, the control force calculation unit 30b multiplies the input longitudinal acceleration G_long by the gain to determine a control force required to prevent pitching of the body B due to inertial force acting in the longitudinal direction.

Then, the control force calculation unit 30b multiplies the input lateral acceleration G_lat by the gain to determine a control force required to prevent rolling of the body B due to centrifugal force.

As described above, the control force calculation unit 30b determines the control forces, on the basis of the bounce rate V_B, the pitch rate the roll rate V_R, the longitudinal acceleration G_long, and the lateral acceleration G_lat. Note that the control forces are determined, designating a sign of a downward force positive, and a sign of an upward force negative. Then, the control force calculation unit 30b determines the body control forces F_FR, F_FL, F_RR, and F_RL which are to be generated from the respective actuators A_FR, A_FL, A_RR, and A_RL, on the basis of these five control forces.

To damp the bounce of the body B, the actuators A_FR, A_FL, A_RR, and A_RL need to generate control forces directed in the same direction and having the same magnitude. To damp pitching of the body B, the front actuators A_FR and A_FL and the rear actuators A_RR and A_RL need to generate control forces having the same magnitude and directed in the opposite directions. To damp rolling of the body B, the right actuators A_FR and A_RR and the left actuators A_FL and A_RL need to generate control forces having the same magnitude and directed in the opposite directions.

Thus, the control force calculation unit 30b adds a control force determined on the basis of the bounce rate V_B, a control force determined on the basis of the pitch rate V_P and the lateral acceleration G_lat and a control force determined on the basis of the roll rate V_R and the lateral acceleration G_long to damp the bouncing, pitching, and rolling of the body B, and determines the body control forces F_FR, F_FL, F_RR, and F_RL which are to be generated from the respective actuators A_FR, A_FL, A_RR, and A_RL. The determined body control forces F_FR, F_FL, F_RR, and F_RL are input to the target control force calculation unit 32.

The road input reduction control calculation unit 31 determines road input reduction control forces F_CFR, F_CFL, F_CRR, and F_CRL on the basis of the vertical accelerations G_UFRG_UFL, G_URR, and G_URL. When the wheels W_FR, W_FL, W_RR, and W_RL vibrate, the suspension springs Sp expand and contract, generating a vibrating force causing the body B to roll and pitch. The road input reduction control forces F_CFR, F_CFL, F_CRR, and F_CRL are each a force for cancelling the vibrating force caused by the expansion and contraction of the suspension spring Sp to vibrate the body B.

When the pitch angle is α, the roll angle is β, a spring constant of a suspension spring Sp of a front wheel is K_F, a spring constant of a suspension spring o£ a rear wheel is K_R, and displacements in a vertical direction (vertical displacements) of the wheels W_FR, W_FL, W_RR, and W_RL are X_UFR, X_UFL, X_URR, and X_URL, pitch moment M_SP and roll moment M_SR caused by forces generated by the suspension springs Sp are expressed by the following (formula 1) and (formula 2).

[Mathematical Formula 1]

M _SP=−2(K_F·L_F²+K_R·L_R²)α+L_F·K_F+(X_UFR+X_UFL)−L_R·K_R·(X_URR+X_URL)  (formula 1)

[Mathematical Formula 2]

M _SR=−(W/2)(K_F+K_R)β+W·K_F·(X_UFR−X_UFL)/2+W·K_R·(X_URR−X_URL)/2  (formula 2)

In each of (formula 1) and (formula 2), the first term on the right side is a restoring force against the rolling or pitching of the body B, and the second term and the third term are considered as moment inputs vibrating the body B upon displacement of the wheels W_FR, W_FL, W_RR, and W_RL.

When forces obtained by multiplying the vertical displacements X_UFR, X_URL, X_URR, and X_URL of the wheels W_FR, W_FL, W_RR, and W_RL by the spring constants K_F and K_R are F_UFR, F_UFL, F_URR, and F_URL, a pitch moment M_P and a roll moment M_R generated by the forces are expressed by the following (formula 3) and (formula 4).

[Mathematical Formula 3]

M _P =L _F·(F_UFR−F_UFL)−L_R·(F_URR+F_URL)  (formula 3)

[Mathematical Formula 4]

M _R =W·(F_UFR−F_URL+F_URR−F_URL)/2  (formula 4)

While, as illustrated in FIG. 4, consider moments M_PC and M_RC cancelling the moments M_P and M_R by applying pitch damping forces F_P having the same magnitude and acting in the opposite directions by the front actuators A_FR and A_FL and the rear actuators A_RR and A_RL of the vehicle V, and applying roll damping forces F_R having the same magnitude and acting in the opposite directions by the right actuators A_FR and A_RR and the left actuators A_FL and A_RL of the vehicle V. Then, the moments M_PC and M_RC are expressed by the following (formula 5) and (formula 6).

[Mathematical Formula 5]

M _PC=2F_P·(L_F+L_R)  (formula 5)

[Mathematical Formula 6]

M _RC=2W·F_R  (formula 6)

To cancel the moments M_P and M_R by the moments M_PC and M_RC, conditions of M_P=M_PC and M_R=M_RC are desirably satisfied. When (formula 5) and (formula 6) are solved for a pitch damping force F_P and a roll damping force F_R while satisfying these conditions, the following (formula 7) and (formula 8) can be derived.

[Mathematical Formula 7]

F _P ={L _F·(F_UFR+F_UFL)−L_R·(F_URR+F_URL)}/{2(L_F+L_R)}   (formula 7)

[Mathematical Formula 8]

F _R=(F_UFR−F_UFL+F_URR−F_URL)/4  (formula 8)

To determine the road input reduction control forces F_CFR, F_CFL, F_CRR and F_CRL to be generated by the actuators A_FR, A_FL, A_RR, and A_RL on the basis of the pitch damping force F_P and the roll damping force F_R determined by (formula 7) and (formula 8) to damp pitching and rolling, designating the sign of a downward force positive, the following (formula 9), (formula 10), (formula 11), and (formula 12) are desirably calculated.

[Mathematical Formula 9]

F _CFR =F _P +F _R  (formula 9)

[Mathematical Formula 10]

F _CFL −F _P −F _R  (formula 10)

[Mathematical Formula 11]

F _CRR =−F _P +F _R  (formula 11)

[Mathematical Formula 12]

F _CRL =F _P −F _R  (formula 12)

The spring constants K_F and K_R of the suspension springs Sp, the distances L_F and L_R from the center of gravity, and the tread W are already given. Furthermore, the vertical displacements X_UFR, X_UFL, X_URR, and X_URL of the wheels W_FR, W_FL, W_RR, and W_RL can be determined only by integrating twice the vertical accelerations G_UFR, G_UFL, G_URR, and G_URL input from the acceleration sensors 26, 27, 28, and 29.

Thus, the road input reduction control calculation unit 31 can determine the road input reduction control forces F_CFR, F_CFL, F_CRR, and F_CRL, on the basis of the spring constants K_F and K_R of the suspension springs Sp, the distances L_F and L_R, the tread W, and the vertical accelerations G_UFR, G_UFL, G_URR, and G_URL.

As illustrated in FIG. 5, the road input reduction control calculation unit 31 includes integrators 40, 41, 42, and 43, multipliers 44 and 45, multipliers 46 and 47, an adder 48, an adder 49, an adder 50, a multiplier 51, a multiplier 52, a multiplier 53, an adder 54, an adder 55, an adder 56, an adder 57, and an adder 58. The integrators 40, 41, 42, and 43 integrate twice the vertical accelerations G_UFR, G_UFL, G_URR, and G_URL input from the acceleration sensors 26, 27, 28, and 29. The multipliers 44 and 45 multiply the vertical displacements X_UFR and X_UFL of the front wheels, which are determined by the integrators 40 and 41, by the spring constant K_F to determine the forces F_UFR and F_UFL. The multipliers 46 and 47 multiply the vertical displacements X_URR and X_URL of the rear wheels, which are determined by the integrators 42 and 43, by the spring constant K_R to determine the forces F_URR and F_URL. The adder 48 adds the forces F_UFR and F_UFL. The adder 49 adds the forces F_URR and F_URL. The adder 50 adds a value obtained by subtracting the force F_URL from the force FU_RR to a value obtained by subtracting the force F_UFL from the force F_UFR. The multiplier 51 multiplies a value output from the adder 48 by L_F/{(2(L_F+L_P)}. The multiplier 52 multiplies a value output from the adder 49 by L_R/{(2(L_F+L_R)}. The multiplier 53 multiplies a value output from the adder 50 by ¼ to determine the roll damping force F_R. The adder 54 subtracts a value output from the multiplier 52 from a value output from the multiplier 51 to determine the pitch damping force F_P. The adder 55 adds the roll damping force F_R to the pitch damping force F_P to obtain the road input reduction control force F_CFR. The adder 56 subtracts the roll damping force F_R from the pitch damping force F_P to determine the road input reduction control force F_CFL. The adder 57 changes the sign of the pitch damping force F_P and adds the roll damping force F_R to the pitch damping force F_P to determine the road input reduction control force F_CRR. The adder 58 changes the signs of the pitch damping force F_P and the roll damping force F_R and adds the pitch damping force F_P and the roll damping force F_R to each other to determine the road input reduction control force F_CFL.

After the vertical accelerations G_UFR, G_UFL, G_URR, and G_URL input to respective units of the road input reduction control calculation unit 31 are processed, calculation from (formula 7) to (formula 12) is performed in the road input reduction control calculation unit 31, and the road input reduction control forces F_CFR, F_CFL, F_CRR, and F_CRL are determined.

The road input reduction control forces F_CFR, F_CFL, F_CRR, and F_CRL obtained as described above are input to the target control force calculation unit 32. As described above, in addition to the road input reduction control forces F_CFR, F_CFL, F_CRR, and F_CRL, the body control forces F_FR, F_FL, F_RR, and F_RL are input to the target control force calculation unit 32.

The target control force calculation unit 32 adds the road input reduction control forces F_CFR, F_CFL, F_CRR, and F_CRL to the body control forces F_FR, F_FL, F_RR, and F_RL, respectively, to determine target control forces F_TFR, F_TFL, F_TRR, and F_TRL for the actuators A_FR, A_FL, A_RR, and A_RL. After determining the target control forces F_TFR, F_TFL, F_TRR, and F_TRL, the target control force calculation unit 32 outputs the target control forces F_TFR, F_TFL, F_TRR, and F_TRL to the drivers 33.

The drivers 33 are provided for the respective actuators A_FR, A_FL, A_RR, and A_RL, and each includes a drive circuit for driving the electromagnetic valve in the hydraulic circuit FC by PWM, and a drive circuit for driving the motor 13 for driving the pump 4 by PWM. When receiving input of commands for the target control forces F_TFR, F_TFL, F_TRR, and F_TRL from the target control force calculation unit 32, each driver 33 supplies current to the electromagnetic valve and the motor 13 in accordance with each command. Note that each drive circuit in the driver 33 may be a drive circuit other than the drive circuit performing the PWM drive.

When the target control forces F_TFR, F_TFL, F_TRR, and F_TRL are a thrust force applied to each cylinder device AC in an extension direction, the controller C controls the electromagnetic valve of the hydraulic circuit FC, to supply the fluid discharged from the pump 4 to the compression chamber R2, and controls the pressure in the compression chamber R2 in accordance with the magnitude of each of the target control forces F_TFR, F_TFT, F_TRR, and F_TRL. In contrast, when the target control forces F_TFR, F_TFL, F_TRR, and F_TRL are a thrust force applied to each cylinder device AC in a contraction direction, the controller C controls the electromagnetic valve of the hydraulic circuit FC to supply the fluid discharged from the pump 4 to the extension chamber R1, and controls the pressure in the extension chamber R1 in accordance with the magnitude of each of the target control forces T_TFR, F_TFL, F_TRR, and F_TRL.

Note that, in the present example, the actuators A_FR, A_FL, A_RR, and A_RL are each a hydraulic actuator including the cylinder device AC and the hydraulic circuit FC, but the actuators A_FR, A_FL, A_RR, and A_RL may be each an electric actuator using a motor. Furthermore, the actuators A_FR, A_FL, A_RR and A_RL may be each a pneumatic actuator pneumatically driven.

As described above, the suspension system S is configured to determine the pitch damping force F_P and the roll damping force F_R for cancelling the roll and pitch moments M_P and M_R of the body B, respectively, determine the target control forces F_TFR, F_TFL, F_TRR, and F_TRL in consideration of the pitch damping force F_P and the roll damping force F_R, and control the actuators A_FR, A_FL, A_RR, and A_RL. When the pitch damping force F_P and the roll damping force F_R are output to the actuators A_FR, A_FL, A_RR, and A_RL, the actuators A_FR, A_FL, A_RR, and A_RL each generate a control force for cancelling a force acting on the body B not later but preliminarily. Thus, the suspension system S according to the present invention can generate a control force for preliminarily damping the vibration of the body B to efficiently damp the vibration of the body B, as compared with a conventional suspension system detecting the vibration of the body B and then generating only a control force for damping the vibration. As described above, in the suspension system S according to the present invention, the vibration of the body B caused by the vibration of the wheels W_FR, W_FL, W_RR, and W_RL can be cancelled, and the body B can have an improved vibration damping effect.

Furthermore, the suspension system S according to the present example is configured to add the road input reduction control forces F_CFR, F_CFL, F_CRR and F_CRL determined on the basis of the pitch damping force F_P and the roll damping force F_R to the body control forces F_FR, F_FL, F_RR, and F_RL for damping detected vibration of the body B, and determine the target control forces F_TFR, F_TFL, F_TRR, and F_TRL. Accordingly, according to the suspension system S of the present example, the control force for preliminarily damping the vibration of the body B can be generated, in addition to the control force for damping the detected vibration of the body B. Thus, in the suspension system S according to the present example, the body B has a considerably improved vibration damping effect, as compared with the conventional suspension system.

Furthermore, the controller C is configured to determine the roll moment M_PC and the pitch moment M_RC which act on the body B, on the basis of the vertical displacements X_UFR, X_UFL, X_URR, and X_URL of the four wheels W_FR, W_FL, W_RR, and W_RL, and determine the pitch damping force F_P and the roll damping force F_P on the basis of the roll moment M_PC and the pitch moment M_RC. When the roll moment M_PC and the pitch moment M_RC which act on the body B are determined on the basis of the vertical displacements X_UFR, X_UFL, and X_URR, the roll moment M_PC and the pitch moment M_RC which act on the body B can be readily and accurately determined on the basis of the vibrations of the four wheels K_FR, W_FL, W_RR, and W_RL. Then, when the pitch damping force F_P and the roll damping force F_R are determined on the basis of thus obtained roll moment M_PC and pitch moment M_RC, a control force can be appropriately generated at appropriate time on the basis of the pitch damping force F_P and the roll damping force F_R, with a reduced calculation load.

Furthermore, the controller C controls the pitch damping forces F_P caused to be generated by the actuators A_FR and A_FL disposed on the front side and the pitch damping forces F_P caused to be generated by the actuators A_RR and A_RL disposed on the rear side to have the same magnitude and to be directed in the opposite directions, and controls the roll damping forces F_R caused to be generated by the actuators A_FR and A_RR disposed on the right side and the roll damping forces F_R caused to be generated by the actuators A_FL and A_RL on the left side to have the same magnitude and to be directed in the opposite directions. Since such a configuration as described above damps the pitching and rolling of the body B without the influence of the vertical vibration on the body B, pitching vibration and rolling vibration of the body B can be reduced considerably.

Note that the vertical displacements X_UFR, X_UFL, X_URR, and X_URL of the wheels W_FR, W_FL, W_RR, and W_RL can be also determined on the basis of the vertical accelerations G₁, G₂, and G₃ detected by the acceleration sensors 21, 22, and 23 provided in the body B and relative displacements between the body B and the wheels W_FR, W_FL, W_RR, and W_RL. In this case, as illustrated in FIG. 6, the relative displacements between the body B and the wheels W_FR, W_FL, W_RR, and W_RL can be obtained with stroke sensors 60, 61, 62, and 63 provided between the body B and the wheels W_FR, W_FL, W_RR, and W_RL. Note that the stroke sensors 60, 61, 62, and 63 may be incorporated into the cylinder devices AC. When the stroke sensors 60, 61, 62, and 63 are provided, the vertical accelerations G_UFR, G_UFL, G_URR, and G_URL of the wheels W_FR, W_FL, W_RR, and W_RL do not need to be detected, and the acceleration sensors 26, 27, 28, and 29 can be eliminated.

The stroke sensors 60, 61, 62, and 63 detect the relative displacements between the body B and the wheels W_FR, W_FL, W_RR and W_RL. Thus, when the displacements of the body B immediately above the wheels W_FR, W_FL, W_RR, and W_RL are given, the vertical displacements X_UFR, X_UFL, X_URR, and X_URL of the wheels can be determined on the basis of the displacements of the body B and the relative displacements.

As described above, on the basis of the vertical accelerations G₁, G₂, and G₃ detected by the acceleration sensors 21, 22, and 23, the bounce rate V_B, pitch rate V_P, and roll rate V_R of the body B can be determined. Integration. of the bounce rate V_B, the pitch rate V_P, and the roll rate V_R can provide vertical displacement X_SG, the pitch angle α, and the roll angle β at the center of gravity of the body B. Since the distances L_F and L_R and the tread W are already given, displacements X_SFR, X_SFL, X_SRR, and X_SRL of the body B immediately above the respective wheels can be determined by calculating the following (formula 13) to (formula 16).

[Mathematical Formula 13]

X _SFR =X _SG +L _F·α+(W/2)·β  (formula 13)

[Mathematical Formula 14]

X _SFL =X _SG +L _F·α−(W/2)·β  (formula 14)

[Mathematical Formula 15]

X _SRR =X _SG −L _F·α−+(W/2)·β  (formula 15)

[Mathematical Formula 16]

X _SRL =X _SG −L _F·α−(W/2)·β  (formula 16)

When relative displacements detected by the stroke sensors 60, 61, 62, and 63 are designated S_FR, S_FL, S_RR, and S_RL, respectively and the following (formula 17) to (formula 20) are calculated using calculation results of (formula 13) to (formula 16), the vertical displacements X_UFR, X_UFL, X_URR, and X_URL can be determined.

[Mathematical Formula 17]

X _UFR =X _SFR −S _FR  (formula 17)

[Mathematical Formula 18]

X _UFL =X _SFL −S _FL  (formula 18)

[Mathematical Formula 19]

X _URR =X _SRR −S _RR  (formula 19)

[Mathematical Formula 20]

X _URL =X _SRL −S _RL  (formula 20)

As described above, the vertical displacements X_UFR, X_UFL, X_URR, and X_URL may be determined on the basis of the vertical accelerations G₁, G₂, and G₃ detected by the acceleration sensors 21, 22, and 23 provided in the body B, and the relative displacements S_FR, S_FL, S_RR, and S_RL detected by the stroke sensors 60, 61, 62, and 63. The vertical displacements X_UFR, X_UFL, X_URR, and X_URL may be determined on the basis o£ the vertical accelerations G, G_UFL, G_URR, and G_URL, or the vertical accelerations G₁, G₂, and G₃ of the body B and the relative displacements S_FR, S_FL, S_RR, and S_RL. Sensors suitable for the body B can be set to determine the vertical displacements X_UFR, X_UFL, X_URR, and X_URL, and the suspension system S can be easily incorporated in the vehicle V.

The preferred embodiments of the present invention has been described in detail above, but modifications, alterations, and changes may be made without departing from the spirit and scope of the present invention.

This application claims the benefit of Japanese Priority Patent Application JP 2015-226990 filed on Nov. 19, 2015, the entire contents of which are incorporated herein by reference.

Claims

1. A suspension system comprising: four actuators interposed between a body of a vehicle and four front and rear, right and left wheels of the vehicle; anda controller for controlling the actuators, whereinthe controller controls the actuators bydetermining a pitch damping force and a roll damping force to cancel roll and pitch moments of the body, respectively, on the basis of vertical displacements of the four front and back, right and left wheels in the vehicle, anddetermining a target control force for each of the actuators on the basis of the pitch damping force and the roll damping force.

2. The suspension system according to claim 1, wherein the controllerdetermines a pitch moment and a roll moment which act on the body, on the basis of the vertical displacements of the four wheels, anddetermines the pitch damping force and the roll damping force on the basis of the pitch moment and the roll moment.

3. The suspension system according to claim 1, wherein the controller controlsthe pitch damping forces caused to be generated by the actuators disposed on the front side in the vehicle and the pitch damping forces caused to be generated by the actuators disposed on the rear side in the vehicle to have the same magnitude and to be directed in the opposite directions, andthe roll damping forces caused to be generated by the actuators disposed on the right side in the vehicle and the roll damping forces caused to be generated by the actuators disposed on the left side in the vehicle to have the same magnitude and to be directed in the opposite directions.

4. The suspension system according to claim 1, wherein the controllerdetermines vertical displacements of the wheels, on the basis of vertical accelerations of the wheels detected by acceleration sensors provided at the wheels, ordetermines vertical displacements of the wheels, on the basis of vertical accelerations of the body detected by acceleration sensors provided in the body, and relative displacements between the body and the wheels detected by stroke sensors provided between the wheels and the body.

5. The suspension system according to claim 1, wherein the controllerdetects vibration of the body to determine body control forces on the basis of the vibration,determines road input reduction control forces on the basis of the roll damping force and the pitch damping force, anddetermines the target control forces by adding the body control forces to the road input reduction control forces.