A vehicle suspension system

Abstract: A vehicle suspension system including a cylinder device provided between a vehicle body member and a vehicle wheel member for the vehicle body member in which suspension characteristics are changed by controlling hydraulic fluid supply (9) for the cylinder device, vehicle height displacement detecting device (14) for detecting a vehicle height displacement, vehicle height control device (17) for receiving a signal from the vehicle height displacement detecting device to control the hydraulic fluid supply for the cylinder device to thereby obtain a target vehicle height displacement in accordance with a height control sensitivity, and sensitivity change device for changing the height control sensitivity in accordance with a predetermined condition so as to change the supply of the hydraulic fluid for the cylinder device. A warp control and a height control are coorperated to be optimized.

Description: BACKGROUND OF THE INVENTION Field of the Invention This invention relates to a vehicle suspension system according to the preamble of claim 1. Such a system is known e.g. from the EP-A-0 306 004, this document relating to an electronic controlled fluid suspension system. Description of the Related Art A conventional active suspension is also disclosed in, for example, Japanese Patent Laid-Open No. 62-96113 laid open to the public on May 2, 1987, European Ptent Application laid open to the public on August 1, 1984 under a publication number 0114757 and U.S. Patent No. 4,371,182 issued on February 1, 1983. In the active suspension as disclosed in the publication enumerated above, a cylinder device is provided for each vehicle wheel member between a vehicle boby member and a vehicle wheel member. By controlling a supply of the hydraulic fluid for the cylinder device, the hydraulic fluid in the cylinder device can be changed so that the vehicle suspension characteristics are changed. In the active suspension system, a hydraulic pressure is detected and a warping of the vehicle body is computed based on the hydraulic pressure detected. A warp control is accompished by controlling a hydraulic fluid supply for the cylinder device. In addition, a vehicle height displacement is detected and a supply of the hydraulic fluid is controlled for the cylinder device to get a target value of the vehicle height displacement (a vehicle height displacement control). The warp control and the vehicle height displacement control are carried out independently. Therefore, both of the controls must be coordinated with each other for improving the suspension property. From the EP-A-0 220 674 there is already known a suspension means comprising an actuator assembly which has a pressure chamber and is adapted to increase or decrease the suspension height of its corresponding vehicle wheel as respective results of supplying or discharging of working fluid to or from its pressure chamber. Further, control means are provided to control the hardness/softness characteristics of the vehicle wheels suspension means to a harder characteristic level and a softer characteristic level. From the cited EP-A-0 306 004 which is also used as a basis for the preamble of claim 1, there is already known a torsional load calculation means for calculating a torsional load applied to the vehicle in response to the suspension load present in the fluid suspension. Further, a compensation control means is provided for determining an undesired torsional load in accordance with the suspension load and calculating a control amount in order to remove the undesired torsional load. Finally, there is disclosed a fluid flow control means responsive to the control amount for controlling the fluid flow to and from a fluid actuator associated with the fluid suspension. SUMMARY OF THE INVENTION An object of the invention is therefore to provide a vehicle suspension system in which both the warp control and the vehicle height displacement control are optimally coordinated with each other to accomplish an improved riding comfort. Another object of the present invention is to provide a responsive active suspension system for the vehicle. The above object of the invention is accomplished by a vehicle suspension system according to claim 1. According to one aspect of the present invention, the sensitivity change means changes the height control sensitivity of the height control means in accordance with a predetermined condition so as to change the supply of the hydraulic fluid for the cylinder device. Thus, both the warp control and the vehicle height displacement control are coordinated to be optimized under the predetermined condition. The height control sensitivity denotes, for example, a gain coefficient of the vehicle height displacement and a dead zone in a vehicle height displacement signal of the vehicle height displacement detecting means. When the gain coefficient of the vehicle height displacement is increased or when the dead zone is reduced, the height control sensitivity is increased. On the contrary, when the gain coefficient is decreased or when the dead zone is increased, the height control sensitivity is reduced. In one of the features of the present invention, the warp control can be emphasized in comparison with the vehicle height displacemennt control by reducing the height control sensitivity under a predetermined condition in which a vehicle speed is increased, a lateral acceleration of the vehicle is increased, or the vehicle is in a parking condition. In another aspect of the present invention, a height change rate control sensitivity can be increased as the height control sensitivity is reduced. The height change rate control sensitivity denotes, for example, a gain coefficient of a vehicle height displacement change rate or a dead zone in a signal of the vehicle height displacement change rate detected or computed based on the vehicle height displacement detecting means. When the gain coefficient of the vehicle height displacement change rate is increased, or when the dead zone in the signal from the vehicle height displacement detecting means is reduced, the height change rate control sensitivity is increased. BRIEF DESCRIPTION OF THE DRAWING Figure 1 is an overall schematic view of a vehicle. Figure 2 is a circuit diagram of a hydraulic system for controlling fluid supply for hydraulic cylinder devices. Figure 3A through 3D are block diagrams illustrating control of suspension characteristics by a controller. Figure 4 and Figure 5 are respectively a first flow chart and a second flow chart of the operation of a vehicle suspension system according to an embodiment of the invention. DESCRIPTION OF THE PREFERRED EMBODIMENT Figure 1 is an overall schematic view of a vehicle according to the invention. In Figure 1, numeral 1 designates a vehicle body member or a vehicle body, and 2F and 2R respectively designate front and rear vehicle wheel members. Between vehicle body 1 and front wheels 2F, and between vehicle body 1 and rear wheels 2R are provided hydraulic cylinders 3 , 3 . A piston 3b inserted into each cylinder body 3a defines a fluid pressure chamber 3c inside each hydraulic cylinder 3. The upper end portion of a rod 3d connected to the piston 3b is connected to the vehicle body 1, and cylinder bodies 3a, 3a are connected to vehicle wheels 2F, 2R respectively. A gas spring 5 is connected to the fluid pressure chamber 3c of each hydraulic cylinder 3 through a communicating path 4. Each gas spring 5 is divided into a gas chamber 5f and a fluid pressure chamber 5g by a diaphragm 5, and the fluid pressure room 5g is connected to the fluid pressure chamber 3c of the hydraulic cylinder 3 through the communicating path 4 and the piston 3b of the hydraulic cylinder 3. Numeral 8 designates a hydraulic pump, and numerals 9, 9 designate proportional flow control valves connected to the hydraulic pump 8 through a fluid pressure path 10. These valves function to control fluid supply for the hydraulic cylinders 3, 3 . Numeral 12 designates a discharge pressure gage which senses the discharge pressure of the hydraulic pump 8, and numerals 13, 13 designate fluid pressure sensors which sense the fluid pressure of the fluid pressure chamber 3c in the hydraulic cylinders 3, 3. Numerals 14, 14 designate vehicle height sensors which sense the vehicle height displacement (cylinder stroke length), and numerals 15, 15, 15 designate vertical acceleration sensors which sense the vertical acceleration of the vehicle (spring acceleration of the wheels 2F, 2R). These vertical acceleration sensors 15, 15, 15 are provided one above each of the right and left front wheels 2F within an approximately horizontal plane, and one at the center of the vehicle in the widthwise direction between the rear wheels 2R. Namely. a total of three vertical acceleration sensors are provided. Numerals 18, 19 designate a steering angle sensor and a vehicle speed sensor, respectively. The signals from the above mentioned sensors are input to a controller 17 constituted of CPU (central processing unit) and the like, which controls the proportional flow control valves 9, 9 so as to change the suspension characteristics. Figure 2 shows a hydraulic circuit for supplying and discharging hydraulic fluid for the hydraulic cylinders 3. As seen in Figure 2, the hydraulic pump 8 is connected in tandem with a hydraulic pump 21 driven by a driving motor 20 for a power steering device. A discharge tube 8a has an accumulator 22 connected with an intermediate portion thereof and a downstream portion of the discharge tube 8a branches off into a front wheel tube 23F and a rear wheel tube 23R. The front wheel tube 23F branches off into a left front wheel tube 23FL and a right front wheel tube 23FR, the downstream ends of which are connected with the fluid pressure chambers 3c, 3c of the hydraulic cylinders 3FL, 3FR. Likewise, the rear wheel tube 23R branches off into a left wheel tube 23RL and a right wheel tube 23RR, the downstream ends of which are connected with the fluid pressure chambers 3c, 3c of the hydraulic cylinders 3RL, 3RR. The gas spring devices 5FL through 5RR connected with the hydraulic cylinders 3FL through 3RR each has a plurality (four) of gas springs 5a, 5b, 5c, 5d which are connected through branch communicating paths 4a through 4d to a common communicating path 4 connected with the fluid pressure chamber 3c of the corresponding hydraulic cylinder 3. The branch communicating paths 4a through 4d of the plurality (first through fourth) gas springs 5a through 5d of each wheel have orifices 25a through 25d. The damping action by the orifices 25a through 25d and the buffer action of gas charged in the gas chambers 5f are combined to provide the basic function as a suspension system. In the gas springs 5FL through 5RR of each vehicle wheel, a damping force switching valve 26 which switches the damping force by adjusting the path area of the communicating path 4 is provided on the common communicating path 4 between the first gas spring 5a and the second gas spring gas spring 5b. The switching valve 26 has two positions: an open position (shown in Figure 2) opening the common communicating path 4 and a throttle position throttling the area of the common communicating path 4. The discharge tube 8a of the hydraulic pump 8 has an unloader relief valve 28 with an open position and a closed position (shown in Figure 2) connected near the accumulator 22. when the discharged fluid pressure measured by the discharge pressure gage 12 is more than and equal to a preset upper limit value, the relief valve 28 is switched from the closed position shown in Figure 2 to the open position, so the fluid in the hydraulic pump 8 is returned directly to a reserve tank 29, whereby the fluid accumulation pressure in the accumulator 22 is controlled to be maintained at a preset value. In above mentioned manner, the accumulated fluid of preset pressure from the accumulator 22 is supplied to the hydraulic cylinders 3. As the left front wheel, the right front wheel, the left rear wheel and the right rear wheel are identical in configurations, only the left front wheel will be described in the following. As explained above, the left front wheel tube 23FL is provided with the proportional flow control valve 9 which has three positions: a stopping position closing all ports (shown in Figure 2), a supplying position where the left front wheel tube 23FL is opened to the supplying side, and a discharge position where the hydraulic cylinder 3 of the left front wheel tube 23FL is connected through a return tube 32. The proportional flow control valve 9 is further provided with pressure-compensated valves 9a, 9a. The pressure-compensated valves 9a, 9a maintain the fluid pressure in the fluid pressure chamber 3c at a preset value when the proportional flow control valve 9 is positioned at either the supplying position or the discharge position. On the hydraulic cylinder 3 side portion of the proportional flow control valve 9 is provided a pilot pressure active type switching valve 33 which opens and closes the left front tube 23FL. When a solenoid controlled valve 34 which introduces the pressurized fluid in the left front wheel tube 23FL is at the open position, the fluid pressure of the solenoid controlled valve 34 is introduced as a pilot pressure to the switching valve 33. When the pilot pressure is more than or equal to a predetermined value, the switching valve 33 operates to open the left front wheel tube 23FL, so that the proportional flow control valve 9 can control the flow to the hydraulic cylinder 3. The numeral 35 designates a relief valve which opens and operates to return the hydraulic fluid in the fluid pressure chamber 3c of the hydraulic cylinder 3 to the return tube 32 when the fluid pressure of the fluid pressure chamber 3c rises abnormally. The numeral 36 designates an ignition switch interlock valve connected near the accumulator 22 on the discharge tube 8a of the hydraulic pump 8. When the ignition switch is at off position, the interlock valve 36 is controlled to open (shown in Figure 2) so as to return the fluid in the accumulator 22 to the tank 29 and relieve the high pressure condition of the fluid. The numeral 37 designates a relief valve which returns fluid to the tank 29 and lowers the fluid pressure when the discharge pressure of the hydraulic pump 8 rises abnormally. The numerals 38, 38 designates return accumulators connected to the return tube 32 for accumulating the fluid discharged from the hydraulic cylinder 3. Figure 3 is a block diagram illustrating control of suspension characteristics by a controller 17. Figure 3 shows a control system A for controlling the vehicle height to a desired value based on vehicle height displacement signals X FR , X FL , X RR , X RL from the vehicle height sensors 14, 14, 14, 14 of the vehicle wheels, a control system B for suppressing vehicle height displacement rates based on the vehicle height displacement rate signals Y FR , Y FL , Y FR , Y RL obtained from the vehicle height displacement signals, a control system C for lowering vertical vibration of the vehicle based on vertical acceleration signals G FR , G FL , G R of the three vertical acceleration sensors 15, 15, 15, and a control system D for supressing vehicle body warping computed from pressure signals P FR , P FL , P RR , P RL of the fluid pressure sensors 13, 13, 13, 13 of the vehicle wheels. First, in the control system A, numeral 40 designates a bounce component arithmetic unit which computes the vehicle bounce components by summing not only the outputs X FR , X FL of the right and left front wheels 2F but also the outputs X RR , X RL of the right and left rear wheels 2R from the vehicle height sensors 14, 14, 14, 14. Numeral 41 designates a pitch component arithmetic unit which computes the vehicle pitch components by subtracting the summed outputs X RR , X RL of the right and left rear wheels 2R from summed outputs X FR , X FL of the right and left front wheels 2F. Numeral 42 designates a roll component arithmetic unit which computes vehicle roll components by summing the difference X FR -X FL of the outputs of the right and left front wheels 2F and the difference X RR -X RL of the outputs of the right and left rear wheels 2R. Numeral 43 designates a bounce control unit which is input the vehicle bounce component computed in the bounce component arithmetic unit 40 and a desired average vehicle height T H , and which computes controlled variables of the proportional flow control valves 9, 9, 9, 9 based on a gain coefficient K B1 under bounce control. Numeral 44 designates a pitch control unit to which is input vehicle pitch components computed in the pitch component arithmetic unit 41 and which computes controlled variables of the proportional flow control valves 9, 9, 9, 9 based on a gain coefficient K P1 under pitch control. Numeral 45 designates a roll control unit to which is input vehicle roll components computed in the roll component arithmetic unit 42 and a desired roll displacement T R , and which computes controlled variables of the proportional flow control valves 9, 9, 9, 9 based on gain coefficients K RF1 , K RR1 under roll control so as to level vehicle height corresponding to the desired roll displacement T R . For the purpose of controlling vehicle height to the desired value, the controlled variables computed in the above mentioned control units 43, 44, 45 are reversed with respect to the signs of the vehicle height displacement signals of vehicle height sensors 14, 14, 14, 14. After that, each controlled bounce, pitch and roll variables for the vehicle wheels are added and flow signals Q FR1 , Q FL1 , Q RR1 , Q RL1 of corresponding proportional flow control valves 9, 9, 9, 9 are obtained in the control system A. Between the vehicle height sensors 14, 14, 14, 14 and the arithmetic units 40, 41, 42 are provided dead zone devices 70, 70, 70, 70, which output their vehicle height displacement signals X FR , X F L , X RR , X RL only when the vehicle height displacement signals X FR , X FL , X RR , X RL from the vehicle height sensors 14, 14, 14, 14 exceed the preset dead zone X H . Next in the control system B, vehicle height displacement signals X FR , X FL , X RR , X RL from the vehicle height sensors 14, 14, 14, 14, are input to differentiators 46, 46, 46, 46, by which differential components of the vehicle height displacement signals X FR , X FL , X RR , X RL , or vehicle height displacement rate signals Y FR , Y FL , Y RR , Y RL are obtained. Here, the vehicle height displacement rate is obtained by the following equation. X n : vehicle height at time t X : vehicle height at time t-1 T : sampling time Numeral 47-1 designates a pitch component arithmetic unit which computes the vehicle pitch elements by subtracting the summation of the outputs Y RR , Y RL of the right and left rear wheels 2R from summation of the outputs Y FR , Y FL of the right and left front wheels 2F. Numeral 47-2 designates a roll element arithmetic unit which computes vehicle roll components by summing difference Y FR -Y FL of the outputs of the right and left front wheels 2F and the difference Y RR -Y RL of the outputs of the right and left rear wheels 2R. Further numeral 48 designates a pitch control unit to which is input the vehicle pitch component computed in the pitch component arithmetic unit 47-1, and which computes controlled variables for the proportional flow control valves 9, 9, 9, 9 based on a gain coefficient K P2 for changing the vehicle height displacement change rate gain under pitch control. Numeral 49 designates a roll control unit which is input vehicle roll components computed in the roll component arithmetic unit 47-2, and which computes controlled variables for the proportional flow control valves 9, 9, 9, 9 based on gain coefficients K RF2 , K RR2 for changing the vehicle height displacement change rate gain under roll control. Thus, each controlled variable computed in the above mentioned control units 48, 49 is reversed with respect to the signs of vehicle height displacement rate signals of the differentiators 46, 46, 46, 46. After that, the controlled pitch and roll variables of the vehicle wheels are added, and flow signals Q FR2 , Q FL2 , Q RR2 , Q RL2 for the corresponding proportional flow control valves 9, 9, 9, 9 are obtained in the control system B. Next in the control system C, numeral 50 designates a bounce component arithmetic unit which computes the vehicle bounce components by summing the outputs G FR , G FL , G R of the three vertical acceleration sensors 15, 15, 15. Numeral 51 designates a pitch component arithmetic unit which computes vehicle pitch components by subtracting the output G R of the rear wheel 2R from the summation of each half-value of outputs G FR , G FL of the right and left front wheels 2F in the three vertical acceleration sensors 15, 15, 15. Numeral 52 designates a roll component arithmetic unit which computes vehicle roll components by subtracting the output G FL of the left front wheel from output G FR of the right front wheel. Further, numeral 53 designates a bounce control unit to which is input vehicle bounce components computed in the bounce component arithmetic unit 50, and which computes controlled variables for the proportional flow control valves 9, 9, 9, 9 of the wheels based on a gain coefficient K B3 under bounce control. Numeral 54 designates a pitch control unit to which is input vehicle pitch components computed in the pitch component arithmetic unit 51, and which computes controlled variables for the proportional flow control valves 9, 9, 9, 9 based on a gain coefficient K P3 under pitch control. Numeral 55 designates a roll control unit to which is input vehicle roll components computed in the roll component arithmetic unit 52, and which computes controlled variables for the proportional flow control valves 9, 9, 9, 9 based on gain coefficients K RF3 , K RR3 under roll control. For the purpose of suppressing vehicle vertical vibration by the bounce components, pitch components and roll components controlled variables in above mentioned control units 53, 54, 55 are reversed in sign in every wheel, and after that, each controlled bounce, pitch and roll variable in each vehicle wheel is added and flow signals Q FR3 , Q FL3 , Q RR3 , Q RL3 for corresponding proportional flow control valves 9, 9, 9, 9 are obtained in the control system C. Between the vertical acceleration sensors 15, 15, 15 and the arithmetic units 50, 51, 52 are provided dead zone devices 80, 80, 80, which output their vertical acceleration signals G FR , G FL , G R only when the vertical acceleration signals G FR , G FL , G R from the vertical acceleration sensors 15, 15, 15 exceed preset dead zone X G . Next in the control system D, a warp control unit 60 includes a fluid pressure ratio arithmetic unit 60a of the front wheel to which is input fluid pressure signals P FR , P FL of the fluid pressure sensors 13, 13 of the two front wheels and computes the ratio (P FR -P FL )/(P FR +P FL ) of the right and left front wheel pressure difference (P FR -P FL ) to the front wheel total fluid pressure (P FR +P FL ), and a fluid pressure ratio arithmetic unit 60b of the rear wheel which similarily computes the fluid pressure ratio (P RR -P RL )/(P RR +P RL ) of the rear wheel. Then after the fluid pressure ratio of the rear wheel is multiplied by a gain coefficient W F , the multiplied value is subtracted from the fluid pressure ratio of the front wheel, thus the subtracted value is multiplied by a gain coefficient W A and moreover is multiplied by a gain coefficient W C in the front wheel. After that, controlled variables for the wheels are reversed in sign for the purpose of being equalized between right and left wheels, so that flow signals Q FR4 , Q FL4 , Q RR4 , Q RL4 of corresponding proportional flow control valves 9, 9, 9, 9 are obtained. Thus, finally total flow signals Q FR , Q FL , Q RR , Q RL are obtained by summing vehicle height displacement components Q FR1 , Q FL1 , Q RR1 , Q RL1 , vehicle height displacement rate components Q FR2 , Q FL2 , Q RR2 , Q RL2 , vertical acceleration components Q FR3 , Q FL3 , Q RR3 , Q RL3 and pressure components Q FR4 , Q FL4 , Q RR4 , Q RL4 finally. Next, in the vehicle suspension system in accordance with the embodiment of the invention, the dead zone X H is changed in the control system A shown in Figure 3, according to predetermined conditions, which are described in detail below. First, Figure 4 shows a first flow chart of a control for the vehicle suspension system in accordance with the present invention. In Figure 4, the procedure starts in step 100. The vehicle speed is read in step 102. When it is found in step 104 that the vehicle speed V is zero (when the vehicle is parked), the dead zone X H is set a value of 5 in step 106. Thus, when the vehicle is parked, the dead zone X H is increased to reduce the sensitivity of the vehicle height control so that use of the frequency of the hydraulic fluid in the accumulator 22 (Figure 2) can be reduced. When the vehicle is parked, the engine is stopped, thus, the oil pump 8 is also stopped so that there is no hydraulic fluid supply for the accumulator 22. On the other hand, if it is judged in the step 104 that the vehicle speed is not zero, the procedure goes to step 108. In step 108, if the vehicle speed V is less than 80km/h(low speed condition of the vehicle), the dead zone X H is set at a value of 1 in step 110. That is, when the vehicle is in a low speed condition, the warp of the vehicle does not affect the steering property of the vehicle seriously. In view of this, the dead zone X H is set at a relatively small value. As a result, the vehicle height control is emphasized to obtain the target vehicle height displacement. When it is judged in step 108 that the vehicle speed is not less than 80km/h, the procedure goes to step 112. In step 112, a judgment is made as to whether or not the vehicle speed is less than 120km/h. If the judgment in step 112 is yes, or if the vehicle speed is less than 120km/h, the dead zone X H is set at a value of 2 in step 114. On the other hand, if it is judged in step 112 that the vehicle speed is not less than 120km/h, the dead zone X H is set at a value of 5 is step 116. Thus, the dead zone X H is increased in a high vehicle speed condition so that the warp control is emphasized compared with the vehicle height displacement control. As a result, the steering property of the suspension system is improved in the high vehicle speed condition. Referring to Figure 5, there is shown a second flow chart of a control of the vehicle suspension system in accordance with the present invention. In Figure 5, the control starts in step 200. In step 202, the vehicle speed V and the steering angle ϑ is read. In step 204, the lateral acceleration is computed based on the vehicle speed V and the steering angle ϑ . When the lateral acceleration G is less than 0.1G, it is judged that the vehicle is running on a straight path (straight running). In this case, the dead zone X H is set at a value of 1 in step 208. That is, when the vehicle is in a low speed condition, the warp of the vehicle does not affect the steering property of the vehicle seriously. In view of this, the dead zone X H is set at a relatively small value. As a result, the vehicle height control is emphasized to obtain the target vehicle height displacement. In step 206, when the lateral acceleration G is not less than 0.1G, it is judged that the vehicle is in a steering operation( steering condition). In this case, the procedure goes to step 210. In step 210, a judgment is made as to whether or not the lateral acceleration is less than 0.3G. If the judgment is yes or if the lateral acceleration G is less than 0.3, the procedure goes to step 212. In step 212, when the vehicle is not in a reverse roll mode, step 214 is carried out and the dead zone X H is increased to a value of 3. If it is judged in the step 212 that the vehicle is in the reverse roll mode, step 216 is carried out and the dead zone X H is set at the value of 1. In other words, the warp control is emphasized by increasing the dead zone X H in a condition other than the reverse roll mode to improve the steering property. On the other hand, the vehicle height displacement control is emphasized by providing the dead zone X H with the relatively small value of 1 to achieve the reverse roll mode. In the step 210, if it is judged that the lateral acceleration G is not less than 0.3G, the procedure goes to step 218 and a judgment is made as to whether or not the lateral acceleration is less than 0.5G. If the judgment is yes or if the lateral acceleration is less than 0.5G, step 220 is carried out and the dead zone X H is set at a value of 4. On the other hand, if the lateral acceleration is not less than 0.5G, step 222 is carried out and the dead zone X H is set at a value of 5. Thus, the dead zone X H is increased as the lateral acceleration G is increased so that the warp control is emphasized compared with the vehicle height displacement control to thereby improve the steering property of the vehicle. In steps 208, 214, 220 and 222, the dead zone X H is set at values of 1, 3, 4 and 5 respectively in a manner that the value of X H is increased as the lateral acceleration is increased. In the same steps 208, 214, 220 and 222, the gain coefficients K RR2 and K RF2 are set at values 0.03, 0.03, 0.05 and 0.07 respectively.

Claims: A vehicle suspension system comprising a plurality of cylinder devices each provided between a vehicle body member (1) and a vehicle wheel member (2F, 2R) whereby suspension characteristics are changed by controlling hydraulic fluid supply/discharge to/from said cylinder devices; a plurality of vehicle height displacement detecting means (14) for detecting the height displacement of said vehicle body member with respect to said vehicle wheel member, vehicle height control means (A) for receiving a signal from the vehicle height displacement detecting means to control the hydraulic fluid supply for the cylinder device to thereby obtain a target vehicle height displacement, said vehicle height control means (A) also including a gain coefficient (K B1 , K P1 , K RF1 , K RR1 ) for modifying said vehicle height displacement signal pressure detecting means for detecting the hydraulic pressure in each of said cylinder devices; warp control means for computing warp of the vehicle body based on said hydraulic pressure detected and for controlling the supply of hydraulic fluid to each of said cylinder devices to thereby suppress warping of the vehicle body characterized in that between each of said vehicle height detecting means and said vehicle height control means (A) are provided dead zone devices (70), which output their vehicle height displacement signals (X FR , X FL , X RR , X RL ) only when said vehicle height displacement signals exceed a predetermined dead zone value (X H ), whereby sensitivity change means are provided for adjusting said dead zone value (X H ) according to predetermined vehicle driving conditions such that as the dead zone value (X H ) is increased or a gain coefficient (K B1 ; K P1 ; K RF1 ; K RR1 ; K RR2 ; K RF2 ) is decreased the warp control of the vehicle is emphasized compared to the vehicle height displacement control. A vehicle suspension system according to claim 1 wherein said sensitivity change means reduces the height control sensitivity as a vehicle speed is increased. A vehicle suspension system according to claim 1 wherein said sensitivity change means reduces the height control sensitivity as a lateral acceleration is increased. A vehicle suspension system according to claim 1 wherein said sensitivity change means reduces the height control sensitivity when the vehicle is in a parking condition. A vehicle suspension system according to claim 1 wherein a sensitivity related to a vehicle height displacement change rate is enhanced as the sensitivity change means changes reduces the height control sensitivity.

Inventors: MORITA TOSHIKI, TAKEHARA SHIN, MORITA, TOSHIKI, TAKEHARA, SHIN
Applicants: MAZDA MOTOR, MAZDA MOTOR CORPORATION
Application year: 1990
Main classification: B60G17
IPC codes: B60G17