ACTIVE VEHICLE SUSPENSION UNIT

Abstract: A hydraulic shock absorber includes a generally vertical cylinder receiving therein hydraulic liquid, a piston working in the cyliner and partioning the interior thereof into two liquid chambers, an upper and a lower chamber. An improved damping control is achieved by a circuit (10) forming a connection between the two liquid chambers (1, 2), a further circuit (9) connecting the reservoir (3) to the lower liquid chamber (2), each of the two circuits (9, 10) including a controllable first check valve (C1) and second check valve (C2), respectively, that can each take two states of operation under the action of a control means (20), in a first state locking the valve in a closed position cutting off the forward flow (E1 and E2 repectively) through the check valve (C1 and C2 respectively), and in a second state allowing a free forward flow (E1 and E2 respectively) through the check valve (C1 and C2 respectively), whereas the check valve (C1, C2) in the first state as well as in the second state block the reverse flow (D1 and D2 respectively) of both circuits (9, 10).

Description: ACTIVE VEHICLE SUSPENSION UNIT Background of the invention The present invention relates to vehicle suspension systems and more particularly, to a vehicle suspension system in which control means incorporating a micro processor or computer controls the damping of a shock absorber to optimize riding and handling characterist¬ ics under a wide range of driving conditions. The control means comprise sensors which provide signals to the micro processor which are representative of the vehicle riding comfort. The control means actively affect the shock absorber operation utilizing programmed algorithms. State of the Art In the US Patent No. 4.154.461, May 15, 1979, a concept ' of a dual state shock absorber for a vehicle wheel is introduced. In said patent there is arranged a throttling valve, combining the upper and lower fluid chambers of a shock absorber cylinder, said valve being fixed in one of two different positions under the influence of an external control means . By this arrangement the shock absorber would offer either "soft", i.e. low .damping or "stiff", i.e. high damping, respectively, to resist either com- pressive or expansive movements of the shock absorber. The decision whether the damping should be stiff or soft is made dependent on the sensor signals y, representing the vehicle vertical velocity (positive upwards), and th signal indicating the compression or expansion sense of the shock absorber as expressed by (y-x) . Here x is the vertical displacement upwards of the wheel and therefore (y-x) is positive for expansion and negative for com- - pression of the shock absorber. It is also shown by said patent that the decision about soft or stiff damping could be made entirely dependent on the sign of the variable S = y*(y-x) . Obviously the arrangement according to said patent would call for two sensors; one sensor being an accelerometer on the car body to yield y and one sensor indicating the com¬ pression or expansion of the shock absorber. The present invention relates to a hydraulic shock absorber including a generally vertical cylinder receiving therein hydraulic liquid, a piston working in the cylinder and partioning the interior thereof into two liquid chambers, an upper and a lower chamber, two sets of one or more damping force generating check valves mounted on the piston, one set generating the damping force in the expansion stroke and another set allowing free flow from the lower to the upper chamber in the compression stroke, a piston rod secured to the piston extending through the end of the cylnder to the outside, said sets of valves constituting connections between the two liquid chambers, a liquid reservoir connected to the lower liquid chamber by a third set of check valves generating the damping force in the compression stroke and allowing a return free flow from the reservoir to the lower chamber in the expansion " stroke. The invention presents a mechanical design to improve the speed and accuracy of the damping control and to simplify the sensor installation. This is achieved by a circuit forming a connection between the two liquid chambers, a further circuit connecting the reservoir to the lower liquid chamber, each of the two circuits including a controllable first check valve and second check valve, respectively, that can each take two states of operation under the action of a control means, in a first state locking the valve in a closed position cutting off the forward flow through the check valve, and in a second state allowing a free forward flow through the check valve, whereas the check valve in the first state as well as in the second state block the reverse flow of both circuits. In a second embodiment the control means comprise a locking device keeping the check valve head in sealing engagement with the valve seat to cut off the forward flow. In a third embodiment the locking device comprises a rocking lever barring the valve head in its sealed engagement in one position and setting the valve head free in one or more further positions. In a fourth embodiment the control means for the check valves comprise electric relays. In a fifth embodiment the control means are under the action of signals from sensors for stating the vertical speed and/or acceleration of the vehicle body or the wheel, said signals being entered into a CPU micro processor comprised in the control means. In a sixth embodiment the control means is programmed to put the check valves in a basic mode or zero mode, Mode 0, when the acceleration signal from the vehicle body or the wheel is within predetermined values, to impart a free state, the second state, allowing free forward flow to both check valves in case the vehicle body acceleration signal is not exceeding a predeterm¬ ined limit value of the acceleration signal, and to impart a locked state, the first state, to both check valves in case the wheel acceleration signal is not exceeding a predetermined limit value of the accelera¬ tion signal. In a seventh embodiment the control means is programmed to put the check valves in a first mode, Mode 1, when any of the acceleration signals exceeds the high limit value, to impart a free, second state to the first check valve and a locked, first state to the second check valve, meaning a soft compression and a stiff expansion of the shock absorber. In an eighth embodiment the control means are programm- ed to put the check valves in a second mode, Mode 2, when any of the acceleration signals passes below the low limit value, to impart a locked, first state to the first check valve and a free, second state to the second check valve, meaning stiff compression and a soft expansion of the shock absorber. In a nineth embodiment the control means are programm¬ ed to retain Mode 1 or Mode 2 for a predetermined time after the acceleration value has reentered within the acceleration tolerance band, defined by the limit values, and after the expiration of the predetermined time to return to Mode 0. In a tenth embodiment the control means are programmed to put the check valves in a third mode, Mode 3, when a signal representing the counting of the number of cycles within a given time interval, exceeds a prede¬ termined value, or the acceleration signal time derivative exceeds a given value, said Mode 3 imparting to both check valves a locked, first state. The invention further teaches principles of electronic control means to balance the conflicting requirements of ride comfort and road holding as well as bringing the suspension control in harmony with braking and steering actions. Drawings The invention will now be described in more detail referring to the drawings in which Figure 1 is a schematic drawing of a shock absorber according to the invention, Figure 2 is a sketch of an upward edge as hit by the wheel, and Figure 3 is a corresponding downward edge. The mechanical design. Reference is made to Figure 1. The patent may be applied to different designs of conventional shock absorbers. Figure 1 refers, however, schematically to an absorber of common design where a piston 6 moves in a cylinder 7. The piston divides the space in the cylinder so as to have an upper chamber 1 and a lower chamber 2. During compression the piston rod 8 is introduced furthe into the cylinder 7, whereby the cylinder cannot contain as much fluid as before. The excess fluid in connection with a compressive movement is transferred to the reser- voir 3. In the compressive movement the main flow resistance is offered by one or more check valves 5. Valves 4 in the piston 6 may or " may not offer an important flow resist- ance to the flux from the lower chamber 2 to the upper chamber 1. At an expansive movement the valves 4 are important " for the damping, whereas opposite valves 5 must not restrict the return flow from the reservoir 3 to chamber 2, which would cause a harmful partial vacuum in chamber 2. The valves 4 and 5 correspond entirely to the throttling of the flow in any conventional shock absorber. They may or may not be springloaded so as to vary their flow cros section as a function of the pressure difference across the valves. The present invention contains two bypass circuits, one for compression, 9, and one for expansion, 10. It should be obvious that an unrestricted circuit 9 would allow th flow under compression to bypass the throttling valve 5, so that the piston 6 would meet a very low degree of damping. The same is true about circuit 10 in expansion, which would bypass the throttling valves 4. Now the bypass circuits 9 and 10 are not unconditionally open and unrestricted for the flow. The circuit 9 is pro vided with a valve Cl and the circuit 10 with a valve C2 Fundamentally these two valves of relief have only two modes, namely free, i.e. unlocked, or locked, i.e. in a closed position. There are of course several valve designs. Thus one arrangement contains relay operated valves, which may be of several alternative designs like "direct relay on valve" or "small valve directly operating a larger slave valve opened by control of pressure by means of the small valve" . However, a very effective and low power valve is now introduced. Here valves Cl and C2 are springloaded check valves, which are closed when the flow is in the direc¬ tions indicated by arrows Dl and D2 respectively. When the flow is in the directions indicated by arrows El or E2, respectively, there could be a flow across the check valves. Those respective flows are, however, con¬ ditioned upon the action of relays Rl and R2. These electromagnetic relays Rl and R2 do not act directly on the valves Cl or C2. Instead they control a locking device, which either fix the valves in a closed position or leave the valves free tc open when subjected to a pressure difference by a flow in the El or E2 direction. The construction of the locking device may follow differ¬ ent design principles. One could be a pair of jaws as in a tool (pincers, pliers) with a very small and effective motion. Another tested design is indicated in Figure 1 and consists of a small springloaded lever 11 or 12, which may be placed in any of two positions 11-11', 12- 12' by the respective relay Rl or R2. This locking design requires a very small amount of power since the relay does not work against the fluid pressure. The motion need not be large and the locking mechanism has very small inertial forces. Switch times of the order of a few milliseconds are easily achieved with this kind of locking devices. Control means The control means for the shock absorber of the active vehicle suspension unit consist of one or two sensors -.-I s an 21' electronic microprocessor unitACPU) and a power circuit to activate the relays Rl and R2. The basic sensor needed to control the shock absorber for one wheel in a given vehicle is an accelerometer. This sensor may be attached to the car body immediately above the wheel, Embodiment I, or it may be fixed to the wheel support, i.e. to the unsprung mass, Embodiment II. In Embodiment I a second sensor is used to count the number of cycles of the shock absorber (from compression to expansion and back to compression) in a given short time interval. This second sensor could be of different types. Thus a simple pressure sensor in circuit 9 or a limit switch device, preferably contactless, on Cl would suffice. The relay switch time is easily decreased considerably by using a capacitor charge power circuit which gives the relay a momentary current much larger than the relay would withstand in steady state. The microprocessor unit -'comprises an A/D circuit to con¬ vert the accelerometer analogue signal into a digital signal to be processed by the CPU. Further the CPU unit has a ROM memory containing one or more programs according to the selected control principle of different modes of operating the active vehicle suspension unit. Therefore the electronic unit primarily comprises several input ports for the sensor(s), an A/D circuit, a CPU, a permanent memory ROM and two output ports to activate the power circuits of the relays Rl and R2. Control principles . When the vehicle is running along a smooth, flat road one desires the suspension system to operate in a fundamental mode, the zero mode or MODE 0. Depending upon where the sensor/accelerometer is placed the fundamental mode will be defined differently. The desirable general behaviour of the shock absorber requires that the fundamental Mode 0 will be abandoned temporarily when the wheel is negoti- ating an upward or a downward edge, see Figure 2 and Figure 3 respectively. Thus, consider what happens when a wheel passes an upward and a downward edge respectively. When the wheel hits the upward edge of Fig. 2 the shock absorber will be rapidly compressed and the vehicle will be pressed upwards. It is obviously desirable that the shock absorber will absorb the obstacle with a minimum of resisting force, i.e. the damping should be low or soft. Passing an upward edge y is positive and (y - x) is nega¬ tive and therefore S = y(y-x) is a negative quantity. In the final phase when the wheel has passed the upward edge the vehicle body will still be moving upwards (y>0) and "overshoot" the final equilibrium level when the spring recoils and the shock absorber is exρanding ; (y-x)>0 . One would like to prevent this overshoot by exerting a stiff damping force. Since the compression has changed to expansion the sign of S has also changed and become posi- tive. When passing a downward edge as indicated in Figure 3 the wheel will tend to loose contact with the road surface. The shock absorber is expanding and the vehicle body tends to fall. At this instant we like the expansion to be rapid to restore the contact quickly. The sign of S is negative since y is negative and (y - x) is positive. Again we see that the desired soft damping is indi¬ cated by the negative sign of S. Finally in the ulti¬ mate phase of the passage of the downward edge there will be a tendency to "overshoot" so that the car has a movement to "bottom" into the shock absorber. One would like the damping to be stiff and the downward motion y < 0 in combination with the compression, (y - x/ < 0 creates a product of two negative quanti¬ ties, therefore S is positive, once again indicating that we should put on a stiff damping. The conclusion is that the desirable behaviour of the suspension system could be expressed in the following table: TABLE I Required damping at edges Summarizing the above we may immediately translate the results regarding the Mode 0 and the behaviour at an upward edge, Mode 1, and at downward edge, Mode 2, into a corresponding control scheme for the Cl and C2 valves : TABLE II Valve control scheme Valve control given in table II requires that one has integrated the y-signal over time to obtain y. However, it has been found that one could use the acceleration signal y directly in the electronic data processing for the control of the valves, thus making integration unnecessary. The acceleration signal y is obviously an earlier indication of an approaching edge than is the integrated signal y. On the other hand, the acceleration signal is more sensitive and more noisy. This particularly is the case when the sensor is an accelerometer (for x " ) fixed to the un- sprung mass as in Embodiment II. This fact has also been reflected in the design of Mode 0, where Embodiment II has a stiff damping whereas Embodiment I has a soft damping. The detec- tion of an upward edge for Embodiment I is of course somewhat slower than for Embodiment II, because in the first case the sensor is on the car body. How¬ ever, compare the sequence of events for the two embodiments: Embodiment I Transfer_from Mode_0_to Mode_l_, see Table II_. Since Cl is already in the free mode, the first part of the transfer is already done. The second part should have C2 transferred to the locked state, but that can easily be done without complication during the first part of the encounter with the upward edge. Transfe£ from j _Mo_de_0_to Mode_2,_se ^ e_Table_Ij[ The first part calls for a free C2," which is already the case. Again there is time to prepare the locking of the Cl. Embodiment II In Embodiment II, Cl and Cl are locked. Therefore there is no immediate preparedness to meet a rough- ness in the road. Thus the shift of valve mode must occur in the beginning of the first part of the encounter with the edge. However, the sensor is on the wheel and the edge is- detected earlier. Since the control in the practical case is made directly from the acceleration signal the edge will be detected quite early and therefore the result for Embodiment II will be similar to that of Embodiment I. Control to transfer between the different modes_0, 1 and 2 To suppress small, noisy signals from the road and from the different, small scale vibrations in the car body it is necessary to introduce a tolerance band +a m/s 2 of acceleration. Within the tolerance band +a the Mode 0 is to prevail. Outside the band there will be a transfer to Mode 1 or Mode 2. Once a transfer to either one has occurred the new mode will be retained a hold time t^ even after the signal magnitude has returned to stay within the tolerance band. Therefore one has the following scheme in common to both Embodiments: TABLE III Mode changes at accelerations exceeding -a m/s 2' Optimation of suspension characteristics All conventional suspension systems are compromises between the demand for ride comfort and the need for good contact between the wheel and the road (road holding) . The ride comfort is disturbed by the car heaving in a frequency range corresponding to the natural oscilla¬ tion of the car body on its suspension springs. The second natural vibration occurs when the unsprung wheel system flutters on a wash board road with relatively small displacements of the car body. This results in a bad road contact for the wheel. Depending on the ampli¬ tude of the road roughness the shocks imparted by one or several wheels to the car body may be lowering the ride comfort. It is the merit of the present invention that it allows a much more sophisticated approach to the optimation of a vehicle suspension in harmony also with the braking and steering actions and corresponding conditions. The acceleration sensor of Embodiment II" or the pulse counter of Embodiment I would either one enable the electronic unit to recognize the occurrence of wheel flutter. This flutter would occur typically at a natural frequency five times that of the car on its springs . The suppression of the wheel flutter is of course desirable . in order to improve the road holding of the car. We may thus introduce still another Mode 3, with both check valves Cl, C2 in a locked position. Mode 3 is equal to Mode 0 for Embodiment II, but it is conven¬ ient to consider Mode 3 as a separate mode depending on the number n c of pulses counted in a given short time interval, "COUNT", which is tuned individually for any given vehicle model. The microprocessor unit would allow a large number of different combinations to connect road holding with ride comfort, braking or steering actions. Therefore the electronic unit may have several extra input ports relating the suspension to the braking or steering systems. The following Table IV demonstrates the basic scheme for the transfer from Mode 0, 1 or 2 to Mode 3: TABLE IV Modes related to COUNT,

Claims: AMENDED CLAIMS [received by the International Bureau on 3 October 1986 (03.10.86) original claims 1-18 replaced by amended claims 1-17 (6 pages)] 1. (Amended) Vehicle suspension system with one or more shock absorbers, each shock absorber comprising, a hydraulic cylinder, receiving therein hydraulic liquid, a piston working in said cylinder, partitioning the inter- ior of said cylinder into an upper chamber and a lower chamber damping force generating means controlling flow from said upper and lower chambers including adjustable valve means controlled by control means (20) to be in a soft mode to provide soft damping characteristics or in a stiff mode to provide stiff damping characteristics in either the compress¬ ion stroke or the expansion stroke of said schock absorber, said control means, (20) being responsive to signals from sensors (22) for signaling the vertical speed ( , x) and/or acceleration (x, y) of the vehicle body (y) or the wheel (x) , said signal being entered into a signal processor (21) in said control means (20) to impart either of said soft or stiff characteristics by means of said adjustable valve means, comprising a first valve means (Cl, 4, 5) providing a variable damp- ing force in the compression stroke, and a second valve means (C2, 4) providing a variable damping force in the expansion stroke, c h a r a c t e r i z e d in that said first valve means includes a first controllable valve (Cl) which is closed to flow during said expansion strok and which has two states of operation during said compression stroke under the control of said control means (20), namely on one hand a firm state in which the flow path from said lower chamber is restricted to provide a relatively high damping force and, on the other hand a soft state in which the flow path from said lower chamber is relatively unrestricted to provide a relatively low damping force, and said second valve means includes a second controllable valve means (C2) which is closed to flow during said compress- ion stroke and which has two states of operation during said expansion stroke under the control of said control means (20) namely on one hand a firm state in which the flow path from said upper chamber is restricted to provide a relatively high damping force and, on the other hand a soft state in which 5 the flow path from said upper chamber is relatively unrestric ed to provide a relatively low damping force, (Following claims 2-7 correspond to previous claims 3-8) 2. A vehicle suspension system according to claim 1, c h a r a c t e r i z e d by said control means (20) 0 being programed, when the body acceleration is sensed, to put said first and second valve means in a zero mode (MODE 0) when the acceleration signal ( * ) from, the vehicle body is within predetermined values (-a < y < +a), in which zero mode, both said valve means (Cl, C2 ) are placed in their 5 soft states when the vehicle body acceleration signal (_/) is not exceeding predetermined limit values of the accele¬ ration signal (+a). 3. A vehicle suspension system according to claim 1, c h a r a c t e r i z e d by said control means (20) 0 being programed when the wheel acceleration (_T) is sensed, to put said first and second valve means in a zero mode (MODE 0) when the acceleration signal (5?) from the vehicle wheel is within predetermined values (-a < * _? < +a), in which zero mode, both said valve means (Cl, C2) are placed "5_ in said firm states when the vehicle wheel acceleration signal (x) is not exceeding predetermined limit values of the acceleration signal (+a). 4. A vehicle suspension system according to claim or -3, c h a r a c e t r i z e d by said control means 0 (20) being programed to put said first and second valve means in a first mode (MODE 1) when either of the accelera¬ tion signals ( * , x") exceeds the high limit value (+a), to impart said soft state to the first valve means (Cl) and said firm state to said second valve means (C2) to thereby 5 effect a soft compression characteristic and a stiff ex¬ pansion characteristic to said shock absorber. 5. A vehicle suspension system according to claim 2 or 3, c h a r a c t e r i z e d by the control means (20) being programed to put said first and second control- lable valve means in a second mode (MODE 2) when either of the acceleration signals (y, x * ) passes below the low limit value (-a), to impart said firm state to said first valve means (Cl) and a soft state to said second valve means (C2) to thereby effect a stiff compression characteristic and a soft expansion characteristic to said shock absorber. 6. A vehicle suspension system according to claim 4 or 5, c h a r a c t e r i z e d by the control means (20) being programed to retain said first mode (MODE 1) or second mode (MODE 2) for a predetermined time (t. ) after the acceleration value has reentered within the acceleration iθlerance band defined by the limit values (- a and + a) and after the expiration of the predetermined time (t. ) to return to said zero mode (MODE 0). 7. A vehicle shock absorber according to claim 1, c h a r a c t e r i z e d by the control means (20) being programed to put said first and second valve means (Cl, C2) in a third mode (MODE 3) when a signal to said control means representing the counting of the number of cycles (COUNT) within a given time interval exceeds a predetermined value (N ), or the acceleration signal time derivative (x or y) c 3 exceeds a given value (b m/s ) said controller (20) impart¬ ing to both of said valve means (Cl, C2) said firm state. 8. (Amended) Vehicle suspension system with one or more chock absorbers each shock absorber including a generally vertical cylinder receiving therein hydraulic liquid, a piston working in the cylinder and partitioning the interior thereof into two liquid chambers, an upper and a lower chamber, two sets of one or more damping force generating valve means (4) mounted on the piston for regulating flow between the lower (2) and the upper (1) chambers, a piston rod (8) secured to the piston (6) extending through the upper end of the cylinder to the outside, said force generating valve means constituting connections between the two liquid chambers (1, 2), a liquid reservoir (3) connect ed to the lower liquid chamber (2) by a third set of check valves generating a damping force in the compression stroke and allowing a return free flow from the reservoir (3) to the lower chamber (2) in the expansion stroke, c h a r a c t e r i z e d by a circuit (10) forming a connection between the two liquid chambers (1, 2), a further circuit (9) connecting the reservoir (3) to the lower liquid chamber (2), each of the two circuits (9, 10) including a controll¬ able first check valve (Cl) and second check valve (C2), re- spectively, that can each take two states of operation under the action of a control means (20), in a first state locking the valve in a closed position cutting off the forward flow (El and E2, respectively) through the check valve (Cl and C2, respectively), and in a second state allowing a free forward flow (El and E2, respecti ely) through the check valve (Cl and C2, respectively), whereas the check valve (Cl, C2) in the first state as well as in the second state block the reverse flow (Dl and D2, respectively) of both circuits (9, 10) . (-Following claims a—17 correspond to previous claims 10-18) , 9. Vehicle suspension system according to claim 8, c h a r a c t e r i z e d by the control means (20) com¬ prising a locking device keeping the check valve (Cl, C2) head in sealing engagement with the valve seat to cut off the forward flow (El and E2, respectively). 10. Vehicle suspension system according to claim 9, c h a r a c t e r i z e d by the locking device compris¬ ing a rocking lever (11, 12) barring the valve head in its sealed engagement in one position, and letting the valve head free in one or more further positions. 11. Vehicle suspension system according to claim 8, c h a r a c t e r i z e d by that the control means (20) for the check valves (Cl, C2) comprises electric relays (Rl, R2). 12. Vehicle suspension system according to claim 8, c h a r a c t e r i z e d by the control means (20) being under the action of signals from sensors (22) for stating the vertical speed and/or acceleration of the vehicle body or the wheel (y, x, y, x) , said signals being entered into a CPU micro processor (21) comprised in the control means (20) . 13. Vehicle suspension system according to any of claims 8-12, c h a r a c t e r i z e d by the control means (20, 21) being programed to put the check valves (Cl, C2) in a basic mode or zero mode, MODE 0, when the acceleration signal from the vehicle body or the wheel (y and x * , respectively) is within predetermined values (-a < x or y < +a), to impart a free state, the second state, allowing free forward flow to both check valves (Cl, C2) in case the ve¬ hicle body acceleration signal (y * ) is not exceeding a pre- 2 determined limit value of the acceleration signal (+a m/s ), and to impart a locked state, the first state, to both check valves (Cl, C2) in case the wheel acceleration sig¬ nal (x * ) is not exceeding a predetermined limit value of the 2 acceleration signal (+a m/s ). 14. Vehicle suspension system according to any of claims 8-12, c h a r a c t e r i z e d by the control means (20, 21) being programed to put the check valves (Cl, C2) in a first mode, MODE 1, when either of the acceleration signals (y, x.) exceeds 2 the high limit value (+a m/s ), to impart a free, second state to the first check valve (Cl) and a locked, first state to the second check valve (C2), meaning a soft com- pression and a stiff expansion of the shock absorber. 15. Vehicle suspension system according to any of claims 8-12, c h a r a c t e r i z e d by the control means (20, 21) being programed to put the check valves (C1-, C2) in a second mode, MODE 2, when either of the acceleration signals (y, x) pass be- 2 low the low limit value (-a m/s ), to impart a locked, first state to the first check valve (Cl) and a free, second state to the second check valve (C2), meaning a stiff compression and a soft expansion of the shock absorber. 16. Vehicle suspension system according to any of claims 14 or 15, c h a r a c t e r i z e d by the control means (20, 21) being programed to retain MODE 1 or MODE 2 for a predeter¬ mined time (t. sec) after the acceleration value has re- h entered within the acceleration tolerance band, defined by 2 2 the limit values (-a m/s and +a m/s ) and after the ex- piration of the predetermined time (t sec) to return to MODE 0. 17, Vehicle suspension system according to any of claims 8-12, c h a r a c t e r i z e d by the control means (20, 21) being programed to put the check valves (Cl, C2) in a third mode, MODE 3, when a signal representing the counting of the number of cycles (COUNT) within a given time interval exceeds a predetermined value (N ), or the acceleration signal time c 3 derivative ( * or y * ) exceeds a given value (b m/s ), said MODE 3 imparting to both check valves (Cl, C2) a locked, first state.

Inventors: SCHNITTGER JAN R, SCHNITTGER, JAN, R.
Applicants: SCHNITTGER JAN R, SCHNITTGER, JAN, R.
Application year: 1986
Main classification: F16F9
IPC codes: B60G17, F16F9