Abstract:
A fluid powered vehicle seat adjustment system comprising a fluid actuator a source of pressurized hydraulic fluid and a controller. The fluid actuator including first and second inlet/outlet conduits, and the controller selectively controlling and directing pressurized fluid selectively to either the first or second inlet/outlets of the actuator. The actuator further comprising actuator isolation valves associated with each of the first and second inlet/outlets of the actuator. Each actuator isolation valve allowing a flow of fluid from the actuator only when pressurized fluid is supplied to the actuator and other isolation valve in order to prevent movement of the actuator except when pressurized fluid is supplied to the actuator.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
     This application claims priority to Great Britain Patent Application No. 0400604.5 filed Jan. 13, 2004, the disclosures of which are incorporated herein by reference, and Great Britain Patent Application No. 0324558.6 filed Oct. 22, 2003, the disclosures of which are incorporated herein by reference. 
     BACKGROUND OF THE INVENTION 
     The present invention relates to a vehicle seats, and in particular to hydraulically or fluid powered adjustable automotive vehicle seats. 
     Adjustable vehicle seats are provided to comfortably accommodate various sizes and shapes of vehicle occupants. Typically at least the fore and aft position of the seat along with the angle of the seat back are adjustable via suitable adjustment and locking mechanisms. Other adjustment of the seat position, and/or parts of the seat, for example adjustment of the seat height and/or tilt, or of the headrest or lumber support position, may also be provided. The seat adjustment mechanisms may be manually operable, or increasingly some or all may be power operated. Conventionally such power operated adjustment mechanisms comprise separate individual electric motors mounted within the seat driving each adjustment mechanism though suitable gearing. 
     Hydraulic or fluid powered seat adjustment mechanisms in which pressurised fluid provided from a pump, is supplied via a control valve to piston/cylinder actuators to adjust the position of the seat or portions of the seat, have been proposed instead of electric powered systems. Indeed the earliest of such proposals date back a number of years. An example of such a powered hydraulic adjustment systems is described in U.S. Pat. No. 5,435,625. A simple telescopic powered hydraulic seat height adjustment arrangement is briefly described in GB 2,167,494. 
     Hydraulic or fluid powered arrangements offer the prospect of extremely quiet, near silent, operation, without the noisy mechanical gearing. Smooth and almost infinitely variable adjustment is also possible with such hydraulic powered arrangements. 
     In spite of these, and other, advantages of hydraulically powered seat adjustments have not been adopted for widespread automotive vehicle seat use over the considerable number of years since they have initially been proposed. Overall, and although hydraulics are used in other areas in automotive vehicles (for example braking systems), and also in non automotive fields, those skilled in the art of vehicle seat design would not generally from a practical stance consider using hydraulic powered seat adjustment systems. Indeed the conventional trend is away from hydraulics in general in automotive applications and to electric powered systems. A distinction should also be drawn between hydraulic or fluid powered adjustment systems, and the more basic and simple hydraulic locking systems and/or damper arrangements. 
     A particular problem with seat adjustment arrangements, and in particular fluid powered arrangements, for automotive use is to provide adequate locking of the seat adjustment. For automotive use it is a requirement that the seat and seat portions once set are securely locked and fixed under all operating conditions and especially in the event of a vehicle crash. In a vehicle crash or impact large forces can be applied to the seat and seat portions which can generate extremely high pressures within a hydraulic adjustment system, which are significantly above the normal operating pressures and for example may be in the region of  1700  bar. The adjustment system must be capable of withstanding these pressures and maintain the locked position of the seat or seat portion. As a result the pipework, pump, actuators, and control valve need to be significantly oversized, and built to a much higher quality, than is required to simply withstand the normal operating conditions and pressure. This increases the resultant costs. In addition even under normal operating conditions leakage from or within the pipework, control valve and pump can undesirably result in movement of the set seat positions. To prevent this the seals within the pump, pipework and control valves must be built to a high quality and standard with resultant cost implications. 
     To address the problems associated with crash loading and the high pressures generated in fluid powered adjustment systems it has been proposed in co-pending UK patent application number 0324558.6, in the name of Lear Corporation, to incorporate system protection valves within the actuator. These system protection valves are adapted to be activated in the event of the pressure within the actuator exceeding a predetermined level and close off the inlet and outlet of the actuators. This isolates or limits the transmission of high pressures from the actuator to the remainder of the hydraulic system to protect the remainder of the hydraulic system from the excessive pressure which may be generated in the actuators in the event of crash loading. Whilst such system protection valves provide an improvement, and limit the pressures to which the remainder of the hydraulic system is subjected, thereby reducing costs, they do not address the potential problems of locking the actuators during normal use when leakage through the control valves or other associated parts may allow the actuator to undesirably move. 
     U.S. Pat. Nos. 5,743,591, 3,760,911, 3,860,098 and 6,161,633 all disclose various manually operated, unpowered, hydraulic adjustable seat locking arrangements incorporating various manually activated control valves. U.S. Pat. No. 5,743,591further includes a crash sensing system which is normally open and closes in a crash condition. None of these prior proposals however address the above described specifc problems. U.S. Pat. Nos. 6,015,130 and 3,777,617 described non automotive hydraulically adjustable chair arrangements which are very different from automotive adjustable seats and automotive seat requirements. U.S. Pat. No. 5,076,647 discloses a relief valve although this is for a brake system. 
     SUMMARY OF THE INVENTION 
     It is a desirable object of the invention to provide an improved fluid powered automotive vehicle seat adjustment system which addresses the above described problems and/or which offers improvements generally. 
     According to the present invention there is provided a fluid powered vehicle seat adjustment system as described in the accompanying claims. 
     In an embodiment of the invention there is provided fluid powered vehicle seat adjustment system comprising a fluid actuator which includes a pair isolation valves. Each isolation valve is adapted to allow a flow of fluid from the actuator only when pressurised fluid is supplied to the other isolation valve. 
     In particular the fluid powered vehicle seat adjustment system comprises a fluid actuator, a source of pressurised hydraulic fluid, and a controller. The fluid actuator includes a first inlet/outlet conduit and a second inlet/outlet conduit. The actuator is responsive to pressurised fluid directed to and from the first and second inlet/outlets. The controller selectively controls and directs pressurised fluid selectively to either the first or second inlet/outlets of the actuator. The actuator further comprises a first actuator isolation valve associated with the first inlet/outlet of the actuator and a second actuator isolation valve associated with the second inlet/outlet of the actuator. The first and second actuator isolation valves are biassed towards a closed position to close off the respective inlet/outlets and prevent a flow of hydraulic fluid from the actuator through the inlet/outlets, and are adapted to each open and allow a flow of fluid from the actuator via the respective inlet/outlet in response to pressurised fluid being supplied to the other actuator isolation valve of the actuator. 
     The actuator isolation valves isolate the actuator from the remainder of the system and prevent flow of fluid from the actuator except when an adjustment is required and pressurised fluid is supplied. As a result the actuator and so seat position is more securely locked and fixed locally at the actuator, with the possibility of uncontrolled movement of the seat due to leakage from the remainder of the system reduced. The remainder of the system, by the isolation of the actuator is also protected and isolated from any high pressures which may be generated within the actuator during crash loading. Accordingly the remainder of the system does not need to be manufactured to such a high quality and strength to eliminate leakage and/or withstand high pressures generated during crash loading. This reduces costs. 
     Preferably the actuator isolation valves comprise a non-return valve which can be selectively operated to allow a return flow. In particular the non-return valve of one of the first and second actuator isolation valves is selectively operated in response to pressurised fluid supplied to the other of the first and second actuator isolation valves. 
     The actuator isolation valves are preferably operatively interconnected. Specifically there may be an interconnecting control conduit to interconnect the first and second actuator isolation valves and direct pressurised fluid supplied to one of the first and second actuator isolation valves to the other of the first and second actuator isolation valves. 
     The actuator isolation valves preferably each comprise a moveable valve member which is moveable from the closed position to close off the respective inlet/outlet to an open position to allow a flow of fluid via the inlet/outlet. In particular the actuator isolation valves may comprise a ball valve which seats against a seat to close off the respective inlet/outlet. 
     The actuator isolation valves may further comprise a moveable piston which moves in response to pressurised fluid supplied to the actuator to open the actuator isolation valve and allow a flow of fluid from the actuator via the inlet/outlet. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a schematic perspective illustration showing the general disposition of a hydraulic vehicle adjustment system within a vehicle seat; 
         FIG. 2  is a schematic simplified functional illustration of the hydraulic vehicle adjustment system of  FIG. 1 ; 
         FIG. 3  is an illustrative more detailed cross section through one of the actuators shown generally in  FIGS. 1 and 2 ; and 
         FIG. 4  is a further more detailed cross sectional view of the isolation valve at one end of the actuator shown in  FIG. 3 . 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     The present invention is an improvement and development of the hydraulic seat adjustment system described in co-pending UK patent application number 0324558.6 which is incorporated in its entirety herein by reference. 
     Referring to  FIG. 1  there is shown a schematic illustration of the disposition of a hydraulically powered seat adjustment system  10  within an outline of an automotive vehicle seat  2 . 
     The vehicle seat  2  includes a seat back  4  which is pivotally connected to a bottom seat cushion  6 , in a conventional manner, at one end about a horizontal lateral axis  8 . The angle of the seat back  4  can accordingly be adjusted relative to the generally horizontally disposed seat bottom cushion  6  as indicated by arrow A. A pair of seat pivot hydraulic actuators  12   a ,  12   b , one on each lateral side of the seat  2 , are operatively connected between the seat back  4  and seat bottom cushion  6  to adjust, control, and set the angle of the seat back  4 . 
     The seat bottom cushion  6  is slidably mounted to the vehicle floor (not shown) in a conventional manner, for example using a pair of sliding seat tracks or rail assemblies (not shown). This allows the seat cushion  6  and seat  2  to be slid fore and aft as indicated by arrow B. A pair of seat track hydraulic actuators  14   a ,  14   b  are provided to adjust and set the fore and aft position of the seat bottom cushion  6  and seat  2  along the rail assemblies and within the vehicle. 
     It will be appreciated that the seat  2  may be, and preferably is, mounted to provide for other movement and adjustment for example to adjust the height of the vehicle seat  2 , and/or angle and tilt of the seat bottom cushion  6 . The seat  2  may also include further movable portions for example a movable headrest (as indicated by arrow C), and/or adjustable lumber support. Further pairs of actuators, or single actuators, may accordingly be similarly provided for such further adjustable mountings and/or movable portions. 
     The hydraulic adjustment system  10 , and the hydraulic circuit, is shown more clearly in simplified schematic form in  FIG. 2 . In  FIG. 2  only one actuator  12 , 14  of each of the pair of actuators  12   a ,  12   b ,  14   a ,  14   b  is shown for simplicity. The other actuators of the pairs of actuators  12   a ,  12   b ,  14   a ,  14   b  shown in  FIG. 1  are connected in parallel with the respective illustrated actuator. 
     The hydraulic adjustment system  10  comprises a hydraulic pump  18  driven by an electric motor  16 . The pump  18  is connected to and in fluid communication with a control module  20 . The pump  18  supplies pressurised hydraulic fluid via a supply pipe  30  to the control module  20 . The control module  20  includes control valves (not shown) which selectively in use direct and control a flow pressurised fluid supplied from the control module  20  to the respective hydraulic actuators  12 ,  14  via actuator supply/return pipes  32 ,  34 . The control valves are activated by switches  21 ,  23  operated by a user. Supply/return pipes  32 ,  34  also return the hydraulic fluid from the hydraulic actuators  12 ,  14  via the control module  20 , and the control valves  40 , to a reservoir  22  which stores an operating quantity of hydraulic fluid. The hydraulic fluid is supplied from the reservoir  22  to the pump  18  via a pump feed pipe  36  completing the hydraulic circuit. 
     To adjust, for example, the angle of, and recline, the seat back  4  a seat occupant operates the respective switch  21  of the control module  20  mounted and located on the side valance of the seat  2 . This operates the respective control valves within the control module  20  to interconnect and direct hydraulic fluid from the supply pipe  30  to one of the supply/return pipes  32  connected to the seat pivot actuator  12 , and to interconnect and direct hydraulic fluid from the other of the supply/return  32  pipes from the seat pivot actuator  12  to the return pipe  35 . At the same time the switch  21 , movement of the valves, or the pressure change in the supply pipe  30  activates the motor  16  and pump  18  to generate a flow of pressurised hydraulic fluid which is supplied and directed to the seat pivot actuator  12  causing the actuator  12  to extend and recline the seat back  4 . Once the desired reclined position is achieved the occupant releases the switch  21 , which closes the valves and stops the pump  18 . The closed valves prevent flow of fluid from the supply/return pipes  32  thereby preventing further movement of the seat pivot actuator  12  and so secure and lock the seat back  4  in the desired position. To move the seat back  4  to a more upright position the switch  21  is moved in the opposite sense, or a second switch is pressed, which operates the valves to direct and interconnect the supply/return pipes  32  to the supply  30  and return  35  in the opposite manner to produce an opposite flow of hydraulic fluid such that the pivot actuator  12  retracts moving the seat back  4  to a more upright position. Adjustment of the fore and aft position and seat track actuators  14 , as well as any other adjustment provided by any further actuators is similar. 
     The hydraulic circuit preferably operates at a relatively low hydraulic pressure, typically  20  bar and can be contrasted with conventional hydraulic systems which generally operate at much higher pressures. This low operating pressure reduces costs since the system primarily only needs to be sized to accommodate this low pressure, and at such a low pressure sealing is much simpler than at higher pressures. 
     The control module may comprise the control module as described in co-pending UK patent application number 0324552.9 filed on 22 Oct. 2003 the contents of which are incorporated in their entirety herein by reference. 
     An electronic control unit  24  is preferably operatively connected to the motor  16 , control module  20  and various other sensors (not shown), to monitor and control the operation of the hydraulic adjustment system  10 . The electronic control  24  unit may also include a memory unit to store previously set seat positions for different occupants and a control unit arranged to operate (via suitable solenoids) the control valves in place of, or in addition to, the manual switches  21 , 23 . Such electronic control units  24  with memory units and arranged to operate powered seat adjustment systems are in themselves known in the art for use with conventional electromechanical seat adjustment systems and can be adopted and used with the above described hydraulic system  10 . 
     The hydraulic actuators  12 , 14  comprise a hydraulic piston  50  mounted within a cylinder  52  defining separate chambers  54 , 56  on either side of the piston  50  as shown in  FIG. 3 . The cylinder  52  is closed off by end caps  40 , 42 . The piston  50  is connected to a piston rod  48  which extends axially through one of the end caps  42 . The end of the piston rod  48  and actuator  12 , 14  are operatively attached to the seat or seat portions to be adjusted, for example between the seat bottom cushion  6  and floor, or between the seat bottom cushion  6  and seat back  4  such that extension and retraction of the actuator  12 , 14  adjusts the seat or seat portion position. Ducts  44 , 46  defined within the respective end caps  40 , 42  connect to and provide inlet/outlets to the respective chambers  54 , 56  of the actuator  12 , 14 . A pair of actuator isolation valve assemblies  60 , 62 , one at each end and for each duct  44 , 46 , selectively close off the respective ducts  44 , 46  as will be explained in further details below. The supply/return pipes  32 , 34  are connected to respective ends of the actuator  12 , 14  to supply and return hydraulic fluid to and from the chambers  54 , 56  on either side of the piston  50  via the actuator isolation valve assemblies  60 , 62 . The actuator  12 , 14 , and in particular piston rod  48 , extends and retracts in response to hydraulic fluid supplied and flowing to and from the actuator  12 , 14  via the supply/return pipes  32 , 34  and into and out of the chambers  54 , 56  of the actuator  12 , 14 . Extension and retraction of the actuator  12 , 14  adjusts the position of the seat  2  or respective seat portion  4 , 6  to which the actuator  12 , 14  is connected. 
     Both of the actuator isolation valve assemblies  60 , 62  of each actuator  12 , 14  are similar, and one of the actuator isolation valve assemblies  62  is shown in more detail in  FIG. 4 . As shown the actuator isolation valve assembly  62  includes a ball valve  70  comprising a ball  68  which is biassed and urged by a coil biassing spring  67  to seat and abut against an annular seat face  66  around a central flow passage  64  interconnecting the inlet/outlet duct  46  to the supply/return pipe  32 , 34  to thereby close off the flow passage  64 . The ball valve  70  is thereby biassed to, and normally, prevents a flow of hydraulic fluid from the actuator chamber  56  through the duct  46  to the supply/return pipes  32 , 34 . The hydraulic fluid is accordingly contained within the actuator  12 , 14  and actuator chamber  56  thereby preventing movement of the piston  50 , actuator and respective seat adjustment. 
     When, during powered seat adjustment, pressurised hydraulic fluid is supplied to the actuator  12 , 14  via one of the supply/return ducts  32 , 34  the pressurised hydraulic fluid acts on the ball  68 , overcoming the biassing force of the biassing spring  67  unseating the ball  68  from the seat face  66  and allowing the pressurised hydraulic fluid to freely flow via the flow passage  64  into the inlet/outlet duct  46  and into the actuator  12 , 14  and actuator chamber  56 . At the same time the pressurised hydraulic fluid supplied from the supply/return duct  32 , 34  flows into and through a central axial bore  74  defined within an isolating valve piston  72  slidably mounted within a isolating valve bore  76 , over and around a piston ball  78  located within the piston bore  80  and across to a control port  82  of the isolating valve assembly  62 . The control port  82  of the first isolating valve assembly  62  is connected via an interconnecting pipe or duct  84  to a corresponding control port  82  of the other, second, actuator isolating valve assembly  60  of the actuator  12 , 14 . The pressurised hydraulic fluid thereby supplied to the control port  82  of the second actuator isolating valve assembly  60  from the first isolating valve assembly  62  urges the second piston ball  78  of the second isolating valve assembly  60  piston  72  (to the right as shown in  FIG. 4 ) against its biassing spring  84  (which may be omitted to improve sensitivity and response) to seat against a piston seat face  86 . This seals off the central bore  74  of the piston  72  of the second isolating valve  60  such that the pressurised hydraulic fluid supplied to the second actuator control port  82  is applied to the whole of the end of the piston  72  of the second isolating valve assembly  60 . This moves and urges the piston  72  axially (to the right as shown in  FIG. 4 ) against its biassing spring  88  towards the ball  68  of the ball valve assembly  70  of the second isolating valve assembly  60  such that a tip end  90  of the piston  72  abuts against and unseats the ball  68  from its seat  66  against its biassing spring  67 . The piston  72  thereby acts as an operating, and override element and means to operate and open the ball valve  70  and isolating valve  60 , 62 , overriding the normal biassing of the valve  70  to the closed position for flow from the actuator and actuator chamber  56 . As a result the ball valve  70  of the second isolating valve  60  is automatically opened and hydraulic fluid can then flow from the chamber  54  via the inlet/outlet duct  44  through the flow passages  64  of the second actuator isolating valve  60  to the supply/return pipe  32 , 34 . This enables the actuator piston  50  to move, as shown in  FIG. 3  to the left, and retracts the actuator  12 , 14  as pressurised hydraulic fluid flows into the right hand chamber  56  and out of the left hand chamber  54 . 
     When pressurised hydraulic fluid is supplied to the other of the supply and return ducts  32 , 34  for the opposite movement and adjustment, the above described operation is simply reversed with the pressurised hydraulic fluid supplied at the second isolating valve opening the first isolating valve to allow hydraulic fluid to then flow out from the actuator chamber  56 , and extension of the actuator  12 , 14 . 
     This arrangement of actuator isolating valve assemblies  60 , 62  isolates the actuator  12 , 14  from the remainder of the hydraulic adjustment system  10  when no pressurised hydraulic fluid is supplied to the actuator (i.e. in the normal fixed non operative position) and prevents the flow of hydraulic fluid from the actuator  12 , 14 . As a result the actuator  12 , 14  position, and so seat adjustment position, is thereby securely fixed and the actuator  12 , 14  locked regardless of any leakage from the remainder of the system  10 . When pressurised fluid is then supplied to one of the supply/return pipes  32 , 34  to operate the actuator  12 , 14  and provide a required seat adjustment the respective isolating valve assembly  60 , 62  allows the pressurised fluid to flow into the actuator  12 , 14  whilst automatically also operating and opening the other isolating valve assembly  62 , 60  to enable hydraulic fluid to flow from the actuator  12 , 14  allowing the actuator  12 , 14  to extend or retract as required in response to the supplied pressurised hydraulic fluid. Once the supply of pressurised hydraulic fluid is terminated the isolating valve assemblies  60 , 62 , by virtue of the biassing adopt their normal positions (as shown in  FIG. 4 ) closing off and isolating and locking the actuator  12 , 14  again. 
     The actuator isolating valve assemblies  60 , 62  thereby act in addition to the control valves of the control module  20  to more securely lock the actuator  12 , 14  and securely fix and lock the position of the seat  2  or respective seat portion  4 , 6  to which the actuators  12 , 14  are connected. In addition the isolating valve assemblies  60 , 62  isolate and protect the remainder of the hydraulic system  10  from any high pressure which may be generated within the actuator and actuator chambers  54 , 56  in the event of and due to crash loading. Indeed in such a case the pressure within the actuator  12 , 14  urges the ball valve  70  more firmly against its seat face  66  further improving the seal closing off the flow passage  64  and flow of fluid from the actuator  12 , 14 . As a result only the actuator  12 , 14  and isolating valve assemblies  60 , 62  need to be designed to withstand the possible high crash loading pressures. 
     It will be appreciated that other isolating valve arrangements to provide similar functionality could alternatively be used in other embodiments. The above described arrangement is though particularly advantageous and is the preferred arrangement. 
     The actuators  12 , 14  in the described embodiments comprise piston and cylinder arrangements, and this is the typical actuator arrangement used for hydraulic vehicle seat adjustment. Other actuator arrangements could of course be used in conjunction with the suitable isolating valve assemblies in accordance with the invention. 
     It will be appreciated that a number of further detailed modifications of the basic arrangements described and shown can be made. In addition the invention can also be applied to pneumatic adjustment systems. 
     In accordance with the provisions of the patent statutes, the principle and mode of operation of this invention have been explained and illustrated in its preferred embodiments. However, it must be understood that this invention may be practiced otherwise than as specifically explained and illustrated without departing from its spirit or scope.