A VEHICLE ROLL STABILISING SYSTEM

Abstract: A vehicle roll stabilising system uses front and rear stabiliser assemblies (23, 34) which each use a stabiliser bar (24) and a hydraulic ram (33, 35) to resist vehicle roll. Selector valves (43, 44) select pressure from a pump (36) or return hydraulic oil to a reservoir (37) according to mode. A diverter valve (73) operates to control the pump pressure in proportion to lateral acceleration to provide an actuator effort which resists roll during vehicle cornering. This effort is provided up to a limit equivalent to a lateral acceleration of approximately 0.4g after which roll is allowed to increase, either by keeping the pump pressure (and hence effort) constant or by increasing the pump pressure at a reduced rate.

Description: A Vehicle Roll Stabilising System This invention relates to vehicle roll stabilising systems of the kind in which an actuator operatively connected to sprung and unsprung portions of the vehicle is arranged so that roll of the vehicle due to lateral acceleration of the vehicle tends to cause displacement of the actuator, the actuator is operable in use to exert an effort in opposition to such displacement and so counteract the roll,. Such a system is known for example from WO-A- 89/04262. It is an object of the invention to provide an improved roll stabilising system for a vehicle. According to one aspect of the invention there is provided a roll stabilising system for a vehicle having front and rear wheels, a front suspension resiliently supporting vehicle weight on the front wheels and a rear suspension resiliently supporting vehicle weight on the rear wheels, the stabilising system including an actuator operatively connected to sprung and unsprung portions of the vehicle and arranged so that roll of the vehicle due to lateral acceleration of the vehicle tends to cause displacement of the actuator, the actuator being operable in use to exert an effort in opposition to such displacement and so counteract the roll, the system further including electronic control means operatively connected to the actuator to control the actuator effort in response to the lateral acceleration such that the actuator effort generally increases with increasing lateral acceleration, the increase in actuator effort being at a rate which is variable according to the magnitude of the lateral acceleration. Preferably the actuator effort increases in direct proportion to the vehicle lateral acceleration up to a predetermined magnitude of lateral acceleration, in which case the actuator effort can be substantially equal to that required to maintain the vehicle level during cornering. Beyond said predetermined magnitude, the actuator effort can remains constant when lateral acceleration is increased, i.e. the rate of increase of actuator effort with the lateral acceleration reduces to zero. However, in a preferred arrangement, the actuator effort continues to increase in direct proportion to the lateral acceleration but at a reduced rate. In this case the actuator effort may be arranged to remain constant when the lateral acceleration is increased beyond a second predetermined magnitude. The predetermined magnitude of lateral acceleration is typically in the range 0.3 to 0.6g, e.g. around 0.5g in the case where the actuator effort remains constant when lateral acceleration is increased and around 0.4g in the case where the actuator effort continues to increase in direct proportion to lateral acceleration at the reduced rate. Where the actuator effort is arranged to remain constant when lateral acceleration is increased beyond a second predetermined magnitude, the second predetermined magnitude of lateral acceleration is typically l.Og. There may be a first actuator associated with the front wheels and a second actuator associated with the rear wheels. This enhances the vehicle stability during cornering by keeping the proportional share of the vehicle weight carried by each of the front wheels substantially the same as that of each of the rear wheels. Conveniently the or each actuator comprises a double acting hydraulic device having first and second inlet/outlet ports, valve means being provided for controlling flow of hydraulic fluid from a source of hydraulic pressure to a drain, the valve means being operable in a first mode in which the first inlet/outlet port is connected to the source and the second inlet/outlet port is connected to the drain and in a second mode in which the second inlet/outlet port is connected to the source and the first inlet/outlet port is connected to the drain, and pressure modulating means is provided to modulate the pressure of the hydraulic fluid supplied by the source to the valve means and thereby control the actuator effort. The first and second modes are the normal operating modes for the valve means when the stabilising system is active to reduce or prevent roll, the first and second modes being selected according to the direction of cornering. Where there is a first actuator associated with the front wheels and a second actuator associated with the rear wheels, said valve means can be common to both actuators. This arrangement equalises the pressures at both actuators, thereby keeping the proportional share of the vehicle weight carried by each of the front wheels the same as that of each of the rear wheels, as discussed earlier. If the flow rate of the hydraulic fluid supplied by the source is limited, the pressure modulating means may conveniently comprise a diverter valve which diverts some of the hydraulic fluid supplied by the source to the drain. The diverter valve may comprise an electrically driven proportional valve in which the restriction to hydraulic flow from the source to the drain varies proportionally with the driving electrical current. Preferably, the valve means comprises first and second selector valves, each selector valve having a supply port for connection to the source, a return port for connection to the drain, a first control port connected to one of the inlet/outlet ports of the or each actuator and a second control port connected to the other of the inlet/outlet ports of the or each actuator, each selector valve having an off condition in which communication between the supply and drain ports and the control ports is prevented and an on condition in which, in the first selector valve, the supply port is connected to the first control port and the second control port is connected to the return port and, in the second selector valve, the supply port is connected to the second control port and the first control port is connected to the return port, the arrangement being such that, in the first mode, the first selector valve is in the on condition and the second selector valve is in the off condition and, in the second mode, the first selector valve is in the off condition and the second selector valve is in the on condition. Such an arrangement of first and second selector valves can be used in other vehicle roll stabilising systems. Hence, according to a second aspect of the invention, there is provided a roll stabilising system for a vehicle having front and rear wheels, a front suspension resiliently supporting vehicle weight on the front wheels and a rear suspension resiliently supporting vehicle weight on the rear wheels, the stabilising system including an actuator operatively connected to sprung and unsprung portions of the vehicle and arranged so that roll of the vehicle tends to cause displacement of the actuator, the actuator comprising a double acting hydrauHc device having first and second inlet/outlet ports and being operable in use to exert an effort in opposition to such displacement and so counteract the roll, the system further including valve means for controlling flow of hydrauHc fluid from a source of hydraulic pressure to a drain, the valve means being operable in a first mode in which the first inlet/outlet port is connected to the source and the second inlet/outlet port is connected to the drain and in a second mode in which the second inlet/outlet port is connected to the source and the first inlet/outlet port is connected to the drain, and pressure modulating means to modulate the pressure of the hydrauHc fluid suppHed by the source to the valve means and thereby control the actuator effort, the valve means comprising first and second selector valves each having a supply port for connection to the source, a return port for connection to the drain, a first control port connected to one of the inlet/outlet ports of the actuator and a second control port connected to the other of the inlet/outlet ports of the actuator, each selector valve having an off condition in which communication between the supply and drain ports and the control ports is prevented and an on condition in which, in the first selector valve, the supply port is connected to the first control port and the second control port is connected to the return port and, in the second selector valve, the supply port is connected to the second control port and the first control port is connected to the return port, the arrangement being such that in the first mode the first selector valve is in the on condition and the second selector valve is in the off condition and in the second mode the first selector valve is in the off condition and the second selector valve is in the on condition.. As described above in relation to the first aspect of the invention, where there is a first actuator associated with the front wheels and a second actuator associated with the rear wheels, said valve means can be common to both actuators. Because each selector valve has only two operative states, each can be of relatively simple construction. The valve means may be operable in a third mode in which the inlet/outlet ports are blocked and in a fourth mode in which the inlet/outlet ports are interconnected, the arrangement being such that, in the third mode, both selector valves are in the off condition and, in the fourth mode, both selector valves are in the on condition. When the valve means is in the third mode, the actuator can act as a direct mechanical interconnection (i.e. is locked solid) and the actuator is active to resist (but not necessarily prevent) roll. This mode is useful as a fail-safe mode under normal driving conditions on good roads. In the fourth mode of the valve means the actuator can be moved freely through the fuU extent of its operating travel. This is useful if the vehicle is operating under extreme off-road conditions since it provides the least resistance to articulation of the front and rear suspensions. Preferably each selector valve is spring biased into the off condition. This is the condition for the third mode which can thereby be achieved in the absence of power to drive the selector valves. Conveniently there is a restricted flow path between the inlet/outlet ports of the actuator. This is useful for the third mode condition of the valve means if there are unequal side to side deflections of the front and rear suspensions of the vehicle. The actuator can then effectively act as a dashpot to aUow the front and rear suspensions to move the vehicle into an upright static position, the actuator being aUowed to move to its mid position. Where the actuator includes an actuating piston the flow path may be through or past the piston. The or each actuator may be associated with a respective stabiHser assembly comprising a stabiHser bar and the actuator, the or each stabiHser assembly having connections adjacent each end of the stabiliser bar to connect the stabiHser assembly to adjacent sprung and unsprung portions of the vehicle and arranged so that roU of the vehicle causes the connections to move in a manner tending to twist the stabiHser assembly and the actuator effort acting to resist such twist. In a further aspect, the invention also comprises a vehicle incorporating a roU stabilising system according to any preceding aspect of the invention. A roU stabiHsing system according to the invention will now be described by way of example and with reference to the accompanying drawings, in which:- Fig. 1 is an hydrauHc circuit diagram of a roU stabiHsing system according to the invention which also shows diagrammaticaUy certain mechanical elements of the system; Fig. 2 is a perspective view of certain of the mechanical elements shown in Fig. 1; Fig. 3 is a block diagram showing an electronic control system used to control the hydrauHc circuit shown in Fig. 1; Figs. 4 to 7 show part of the hydrauHc circuit diagram shown in Fig. 1 in first, second, third and fourth operating modes respectively; Fig. 8 is a graph showing vehicle roll angle plotted against vehicle lateral acceleration; and Fig. 9 is a graph showing the restoring torque exerted by the roU stabilising system plotted against vehicle lateral acceleration. The roU stabiHsing system shown in Figs. 1 to 7 is for a vehicle which has front wheels 11, 12 carried on a front axle 13 and rear wheels 14, 15 carried on a rear axle 16. The vehicle has a body which is carried on a chassis 17, the vehicle weight being resiliently supported by front suspension units 18, 19 and rear suspension units 21, 22. A front stabiHser assembly 23 includes a stabiHser or anti-roH bar 24 connected to the vehicle chassis 17 by bearing assembHes 25, 26 lateraUy spaced towards each side of the vehicle. The front stabiHser bar 24 has an integral arm 27 which extends in a substantiaUy horizontal direction longitudinally towards the rear of the vehicle. The end of the arm 27 remote from the left hand bearing assembly 25 is connected to the front axle 13 near the left hand wheel 11 by a pivotal Hnk 28. At the other end of the stabiHser bar 24 to the arm 27, a pivot arm assembly 29 is pivoted on the stabiHser bar and carries another pivotal Hnk 31 which connects it to the front axle 13 near to the right hand wheel 12. The chassis 17 is a sprung part of the vehicle whereas the front axle 13 is an unsprung part. A crank arm 32 is securely fastened to the stabiHser bar 24 (e.g. by welding) and extends in a substantially vertical direction, i.e. at approximately right angles to the arm 27 and the pivot arm assembly 29. An actuator in the form of a double acting hydraulic ram 33 is pivotaUy connected to the crank arms 32 and to the pivot arm assembly 29 adjacent to the pivotal Hnk 31. A rear stabiliser assembly 34 is substantiaUy identical to the front stabiHser assembly 23 and has its own hydrauHc ram 35. The hydrauHc rams 33, 35 are arranged to be connected to a source of hydrauHc pressure in the form of an engine driven pump 36 or to a drain in the form of an hydrauHc reservoir 37. Each hydrauHc ram 33, 35 has a piston 38 and an actuating rod 39. On the actuating rod side of the piston 38 there is a first inlet/outlet port 41 and on the other side of the piston there is a second inlet/outlet port 42. Naive means in the form of first and second solenoid-controUed selector valves 43 and 44 are provided to control the flow of hydrauHc fluid from the pump 36 to the inlet/outlet ports 41 and 42 and to control the return flow from the inlet/outlet ports to the reservoir 37. The selector valves 43 and 44 are mounted in a valve block 45 (depicted by dotted Hne). The first selector valve 43 has a supply port 46 which is connected to the pump 36 by a passage 47 in the valve block 45 and by line 48 and has a return port 49 which is connected to the reservoir 37 by passages 51, 52 in the valve block 45 and by Hne 53. The first selector valve 43 also has first and second control ports 54 and 55, the first control port 54 being connected to the first inlet/outlet port 41 of both actuators 33 and 35 through valve block passages 56, 57 and 72 and by Hnes 59 and 61 and the second control port 55 being connected to the second inlet/outlet port 42 of the actuators by valve block passages 62 and 63 and by Hnes 64 and 65. Similarly, the second selector valve 44 has a supply port 66 connected to the pump 36 by a passage 67 connected to valve block passage 47 and a return port 68 connected to the reservoir 37 by valve block passage 52. The second selector valve 44 also has a first control port 69 connected to the second inlet/outlet ports 42 of the hydraulic cyHnders 33 and 35 by valve block passages 58, 62 and 63 and by Hnes 64 and 65. Similarly the second selector valve 44 also has a first control port 71 which is connected to the first inlet/outlet ports 41 of the hydrauHc cyHnders 33 and 35 by valve block passages 72, 57 and 56 and by Hnes 59 and 61. The selector valves 43. 44 are spring biased into an off condition in which direct flow between the ports 46, 49, 54, 55; 66, 68, 69, 71 of each selector valve is prevented. A diverter valve 73 is in a passage 74 connecting passage 47 which takes the main flow of pressurised hydrauHc fluid from the pump 36 and passage 52 which dehvers the return flow to the tank 37. The diverter valve 73 acts as pressure modulating means as wiH be described later. A pressure transducer 75 is connected to the passage 47 by a passage 76 to provide a signal indicative of the pressure suppHed by the pump 36. The solenoid selector valves 43 and 44 and the diverter valve 73 are controUed by an electronic control unit (ECU) 77 which receives a pressure signal from the pressure transducer 75 and a lateral acceleration signal from an accelerometer 78. Signals indicative of other vehicle parameters may be included but these are not relevant to the present invention. The selector valves 43 and 44 aUow for four modes of operation. In the first mode (Fig. 4) the first selector valve 43 is on (solenoid energised) and the second selector valve 44 is off (solenoid de-energised). HydrauHc fluid under pressure can be suppHed by the pump 36 to the first inlet/outlet ports 41 of the hydrauHc rams 33, 35 through the first control port 54 of the first selector valve 43 and hydrauHc fluid from the second inlet/outlet ports 42 of the rams 33, 35 can return to the reservoir 37 through the second control port 55 of the first selector valve. Hence hydraulic pressure suppHed to the rams 33, 35 will tend to move each ram so that the respective actuating rod 39 is retracted into the cylinder and the ram can exert an effort in the form of a tensfle force. In the second mode (Fig. 5) the second selector valve 44 is on (solenoid energised) and the first selector valve 43 is off (solenoid de-energised). HydrauHc fluid under pressure can be suppHed by the pump 36 to the second inlet/outlet ports 42 of the hydrauHc rams 33, 35 through the second control port 69 of the second selector valve 44 and hydrauHc fluid from the first inlet/outlet ports 41 of the rams 33, 35 can return to the reservoir 37 through the first control port 71 of the second selector valve. Hence hydraulic pressure suppHed to the rams 33, 35 wiU tend to move each ram so that the respective actuating rod 39 is pushed out of the cyHnder and the ram can exert a compressive force. The first and second modes are the normal operating modes for when the vehicle is traveUing on ordinary roads. When the vehicle is cornering, centrifugal force tends to cause the vehicle to lean outwards away from the corner. This moves one of the pivotal Hnks 28, 31 upwards relative to the vehicle chassis 17 and the other Hnk 31, 29 downwards relative to the chassis, such movement tending to twist the stabiHser bar assembly 23 by the crank arms 32 moving relative to the pivot arm assembly 29, compressing or extending the hydrauHc rams 33 and 35. Such compression or extension is resisted by the hydrauHc pressure suppHed to the inlet/outlet ports 41, 42 in a manner which resists roll of the vehicle. This wiU be described in more detail later. In the third mode of operation (Figs. 1 and 6) both selector valves 43 and 44 are closed so that the hydrauHc rams 33 and 35 are hydrauHcaUy locked. This is a faU-safe condition suitable for on road use which aUows the stabiHser bar assembly 23 to act in the manner of a conventional stabiHser bar, the stabiliser bar 24 acting as a torsion bar to resist roU of the vehicle. There is a restricted flow path between the inlet/outlet ports 41, 42 of the rams 33, 35 which aUows the front and rear suspension units 18, 19, 21 and 22 to restore the vehicle to an upright condition after cornering over a period of about 5 to 10 seconds, e.g. 7 seconds. In Fig. 1 the restricted flow path is iUustrated by a passage in each piston 38. In practice, leakage flow past the seals of the pistons 38 can provide an appropriate flow path. In the fourth mode (Fig. 7) both selector valves 43 and 44 are in the on (open) condition. The inlet/outlet ports 41 and 42 are interconnected which equaHses the pressures on both sides of the ram pistons 38. The pump 36 is a positive displacement device which, being driven by the engine, has a limited dehvery rate. Fluid can flow from the pump 36 through the selector valves 43 and 44 to the tank so no appreciable pressure is generated. The hydrauHc rams 33 and 35 are free to extend and retract so that each stabiHser assembly 23, 34 is ineffective to resist roU, up to the Hmit of travel of the respective ram 33. This is an appropriate mode for extreme off-road conditions which require the axles 13 and 16 to articulate freely in opposite directions to optimise the ground contact pressure of the wheels 11, 12, 14, 15. The diverter valve 73 is a pulse-width modulation solenoid-controUed flow valve and the pressure transducer 75 aUows for closed loop control of pump dehvery pressure in passage 47. Alternatively, open loop control can be used if the pump is caHbrated and the pump dehvery pressure is inferred from the engine speed and the mark/space ratio of the electrical current driving of the diverter valve 73. During normal use of the vehicle, the accelerometer 78 measures the centripetal (lateral) acceleration of the vehicle and the ECU 77 switches the selector valves 43 and 44 into the first or second mode according to cornering direction. At the same time, the ECU 77 operates the pressure modulating diverter valve 73 to adjust the pump pressure to a magnitude which wiU prevent vehicle roU at that particular acceleration. This provides an initial rate of increase of effort from the actuator rams 33, 35 which continues up to a pump pressure equivalent to a predetermined magnitude of lateral acceleration, e.g. 0.4g. Thereafter, pump pressure continues to increase but at a reduced rate to allow a Hmited amount of body roll. This makes the driver more aware of the vehicle operating conditions, thereby discouraging cornering to the point where tyre adhesion is lost. This is illustrated by Fig. 8 where roU angle R is shown as a function of lateral acceleration L and by Fig. 9 where the restoring torque T exerted by the roU stabilising system as a result of the actuator effort is shown as a function of lateral acceleration L. In Fig. 8 the horizontal Hne A-C shows roU control in operation at the initial rate of increase in actuator effort up to the predetermined magnitude of lateral acceleration at point C. Greater lateral acceleration results in controUed roU at the reduced rate of increase in actuator effort according to the characteristics C-D. The dashed Hne A-B illustrates the characteristics of a conventional vehicle in which roU increases with lateral acceleration under aU normal conditions. In Fig. 9 the steep straight Hne A'-C shows the initial rate of increase in actuator effort and restoring torque up to the predetermined magnitude of lateral acceleration at point C. Greater lateral acceleration results in controUed roU at the reduced rate of increase in actuator effort according to the characteristics C'-D', the reduced rate of increase in restoring torque being reflected by the reduced slope of this Hne. In a particular vehicle incorporating the invention, the Hne A'-C represents 10,000 NM/g and Hne C'-D' represents 2,200 NM/g Beyond a second predetermined magnitude of lateral acceleration, e.g. l.Og the pressure may be held constant to aUow a further increased rate of body roU. This can be achieved by the pressure modulating valve 73 in conjunction with the ECU 77 or by including a pressure reHef valve in the hydrauHc circuit. As an alternative to increasing the actuator effort at a reduced rate when cornering beyond the predetermined magnitude of lateral acceleration, the pump pressure can be kept constant, i.e. the rate of increase reduces to zero. This is illustrated in Fig 9 by the Hnes A'-C" and C'-D". In such a case, the predetermined magnitude of lateral acceleration may be higher, e.g. 0.5g. It wiU be appreciated that the ECU 77 can be programmed to produce any characteristic of actuator effort against lateral acceleration. So, for example, it may be beneficial to graduaUy reduce the rate of increase in actuator effort with lateral acceleration as impHed by Hne A'-E in Fig. 9. Also, it may not be desirable to exactly counteract roU during the initial phase of roU control, i.e. some degree of roU may be required. Indeed, some degree of leaning-in (negative roU) may be desirable. The degree of control wiU be determined by the suspension and handhng characteristics required of the particular vehicle model. Note also that the ECU 77 is also programmed to aUow for different pressure/force characteristics of the rams 33 and 35 according to the direction of cornering, this being caused by the area of the actuating rods 39. Although the selector valves 43, 44 are of simple design and construction, they may be hydraulicaUy operated using solenoid or other electricaUy operated pUot valves. Also, other ways of modulating the pump pressure may be used, particularly if pump pressure is stored in an accumulator and is suppHed to the selector valves through a pressure modulating valve which modulates supply pressure in direct proportion to electrical current. Although the system has been described with stabiHser assembhes on both front and rear suspensions, it may be apphed to only one of the front and rear suspension, albeit to the possible detriment of some of the operational advantages described. The invention is appHcable to both conventionaUy sprung vehicles and to those utilising self-leveUing, either both front and rear or front or rear only. The invention may be used with other arrangements of stabiHser assembly to the one described above, for example one in which a stabiHser bar has two integral arms, one of which is Hnked to an unsprung part of the vehicle by the actuator, or one where the stabiHser bar is in two parts which are Hnked at or near the centre by the actuator. In fact, other ways of utilising the actuator to counteract roU are possible without using a stabiHser assembly with a stabiHser bar. Although a linear actuator has been shown, the invention is equaUy appHcable where a rotary actuator is used.

Claims: CLAIMS 1. A roU stabiHsing system for a vehicle having front and rear wheels (11, 12, 13, 14), a front suspension (18, 19) resUiently supporting vehicle weight on the front wheels and a rear suspension (21, 22) resihently supporting vehicle weight on the rear wheels, the stabiHsing system including an actuator (33) operatively connected to sprung and unsprung portions of the vehicle and arranged so that roU of the vehicle due to lateral acceleration of the vehicle tends to cause displacement of the actuator, the actuator being operable in use to exert an effort in opposition to such displacement and so counteract the roU, the system further including electronic control means (77) operatively connected to the actuator to control the actuator effort in response to the lateral acceleration such that the actuator effort generaUy increases with increasing lateral acceleration, the increase in actuator effort being at a rate which is variable according to the magnitude of the lateral acceleration. 2. A roU stabiHsing system according to claim 1 wherein the actuator effort increases in direct proportion to the lateral acceleration up to a predetermined magnitude of the lateral acceleration. 3. A roU stabiHsing system according to claim 2 wherein, up to said predetermined magnitude of lateral acceleration, the actuator effort is substantiaUy equal to that required to maintain the vehicle level during cornering. 4. A roU stabiHsing system according to claim 2 or claim 3 wherein the actuator effort remains constant when the lateral acceleration is increased beyond said predetermined magnitude. 5. A roll stabUising system according to claim 2 or claim 3 wherein the actuator effort increases in direct proportion to the lateral acceleration beyond said predetermined magnitude but at a reduced rate. 6. A roll stabiHsing system according to claim 5 wherein the actuator effort remains constant when the lateral acceleration is increased beyond a second predetermined magnitude. 7. A roll stabUising system according to any of claims 2 to 6 wherein the predetermined magnitude of lateral acceleration is in the range 0.3 to 0.6g. 8. A roU stabUising system according to claim 7 when dependent on claim 4 wherein the predetermined magnitude of lateral acceleration is approximately 0.5g. 9. A roU stabUising system according to claim 7 when dependent on claim 5 or claim 6 wherein the predetermined magnitude of lateral acceleration is approximately 0.4g. 10. A roU stabUising system according to claim 6 wherein the second predetermined magnitude of lateral acceleration is approximately 1.0 g. 11. A roU stabUising system according to any preceding claim and including a first actuator (33) associated with the front wheels (11, 12) and a second actuator (35) associated with the rear wheels (14, 15). 12. A roU stabUising system according to any preceding claim wherein the or each actuator comprises a double acting hydrauHc device (33, 35) having first and second inlet/outlet ports (41, 42), the roll stabUising system including valve means (43, 44) for controUing flow of hydrauHc fluid from a source of hydrauHc pressure (36) to a drain (37), the valve means being operable in a first mode in which the first inlet/outlet port (41) is connected to the source and the second inlet/outlet port (42) is connected to the drain and in a second mode in which the second inlet/outlet port (42) is connected to the source and the first inlet/outlet port (41) is connected to the drain, and pressure modulating means (73) to modulate the pressure of the hydrauHc fluid supplied by the source to the valve means and thereby control the actuator effort. 13. A roll stabUising system according to claim 12 when dependent on claim 11 wherein said valve means (43, 44) is common to both actuators (33, 35). 14. A roU stabiHsing system according to claim 12 or claim 13 wherein the flow rate of the hydrauHc fluid suppHed by the source (36) is limited and the pressure modulating means comprises a diverter valve (73) which diverts some of the hydrauHc fluid suppHed by the source to the drain (37). 15. A roU stabUising system according to claim 14 wherein the diverter valve comprises an electricaUy driven proportional valve (73) in which the restriction to hydrauHc flow from the source (36) to the drain (37) varies proportionaUy with the driving electrical current. 16. A roU stabUising system according to any of claims 12 to 15 wherein the valve means comprises first and second selector valves (43, 44), each selector valve having a supply port (46, 66) for connection to the source (36), a return port (49, 68) for connection to the drain (37), a first control port (54, 69) connected to one (41) of the inlet/outlet ports of the or each actuator (33, 35) and a second control port (55, 71) connected to the other (42) of the inlet/outlet ports of the or each actuator (33, 35), each selector valve having an off condition in which communication between the supply and drain ports and the control ports is prevented and an on condition in which, in the first selector valve (43), the supply port (46) is connected to the first control port (54) and the second control port (55) is connected to the return port (49) and, in the second selector valve (44), the supply port (66) is connected to the second control port (69) and the first control port (71) is connected to the return port (68), the arrangement being such that, in the first mode, the first selector valve (43) is in the on condition and the second selector valve (44) is in the off condition and, in the second mode, the first selector valve is in the off condition and the second selector valve is in the on condition. 17. A roll stabUising system for a vehicle having front and rear wheels (11, 12, 13, 14), a front suspension (18, 19) resUiently supporting vehicle weight on the front wheels and a rear suspension (21, 22) resUiently supporting vehicle weight on the rear wheels, the stabUising system including an actuator (33) operatively connected to sprung and unsprung portions of the vehicle and arranged so that roll of the vehicle tends to cause displacement of the actuator, the actuator comprising a double acting hydrauHc device (33, 35) having first and second inlet/outlet ports (41, 42) and being operable in use to exert an effort in opposition to such displacement and so counteract the roU, the system further including valve means (43, 44) for controUing flow of hydrauHc fluid from a source of hydrauHc pressure (36) to a drain (37), the valve means being operable in a first mode in which the first inlet/outlet port (41) is connected to the source and the second inlet/outlet port (42) is connected to the drain and in a second mode in which the second inlet/outlet port (42) is connected to the source and the first inlet/outlet port (41) is connected to the drain, and pressure modulating means (73) to modulate the pressure of the hydrauHc fluid suppHed by the source to the valve means and thereby control the actuator effort, the valve means comprising first and second selector valves (43, 44) each having a supply port (46, 66) for connection to the source (36), a return port (49, 68) for connection to the drain (37), a first control port (54, 69) connected to one (41) of the inlet/outlet ports of the actuator (33, 35) and a second control port (55, 71) connected to the other (42) of the inlet/outlet ports of the actuator (33, 35), each selector valve having an off condition in which communication between the supply and drain ports and the control ports is prevented and an on condition in which, in the first selector valve (43), the supply port (46) is connected to the first control port (54) and the second control port (55) is connected to the return port (49) and, in the second selector valve (44), the supply port (66) is connected to the second control port (69) and the first control port (71) is connected to the return port (68), the arrangement being such that in the first mode the first selector valve (43) is in the on condition and the second selector valve (44) is in the off condition and in the second mode the first selector valve is in the off condition and the second selector valve is in the on condition. 18. A roU stabiHsing system according to claim 16 or claim 17 wherein the valve means (43, 44) is operable in a in a third mode in which the inlet/outlet ports (41, 42) are blocked and in a fourth mode in which the inlet/outlet ports are interconnected, the arrangement being such that, in the third mode, both selector valves (43, 44) are in the off condition and, in the fourth mode, both selector valves are in the on condition. 19. A roU stabUising system according to Claim 18 wherein each selector valve (43, 44) is spring biased into the off condition. 20. A roll stabUising system according to any of claims 16 to 19 wherein there is a restricted flow path between the inlet/outlet ports (41, 42) of the or each actuator (33, 35). 21. A roll stabUising system according to claim 20 wherein the or each actuator (33, 35) includes an actuating piston (38) and the flow path is through or past the piston. 22. A roU stabUising system according to any preceding claim wherein the or each actuator (33) is associated with a respective stabiHser assembly (23, 34) comprising a stabiHser bar (24) and the actuator (33), the or each stabiHser assembly having connections (25, 26, 28, 29) adjacent each end of the stabiHser bar to connect the stabiHser assembly to adjacent sprung and unsprung portions of the vehicle and arranged so that roU of the vehicle causes the connections to move in a manner tending to twist the stabiHser assembly and the actuator effort acting to resist such twist. 23. A vehicle incorporating a roU stabUising system according to any preceding claim.

Inventors: BURDOCK WILLIAM, CLARE DAVID ANDREW, GREEN PHILLIP JAMES, PASK MARK, BURDOCK, WILLIAM, CLARE, DAVID, ANDREW, GREEN, PHILLIP, JAMES, PASK, MARK
Applicants: BURDOCK WILLIAM, CLARE DAVID ANDREW, GREEN PHILLIP JAMES, PASK MARK, ROVER GROUP, BURDOCK, WILLIAM, CLARE, DAVID, ANDREW, GREEN, PHILLIP, JAMES, PASK, MARK, ROVER GROUP LIMITED
Application year: 1997
Main classification: B60G17
IPC codes: B60G17, B60G21