Abstract:
A valve assembly comprising a valve body, a first movable pressure responsive element, and a second pressure responsive movable element, wherein the valve assembly further comprises a resilient biasing element and a movable third pressure responsive element, the resilient biasing element extending between the third pressure responsive element and the valve body and the third pressure responsive element being adapted to act on both the first and second pressure responsive elements to transmit the biasing force of the resilient biasing element to both the first and second pressure responsive elements.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     The present application is a continuation of pending International patent application PCT/GB2005/003128 filed on Aug. 10, 2005 which designates the United States and claims priority from United Kingdom patent application 0419239.9 filed on Aug. 28, 2004, the content of which is incorporated herein by reference. 
    
    
     FIELD OF THE INVENTION 
     The invention relates to a valve assembly having electrical means for controlling fluid pressure relative to a working volume in three controls states. The control states may apply, hold or release fluid pressure relative to the working volume. The valve assembly may be an ABS or EBS valve in the brake system of a vehicle in which the control states may apply, hold or release fluid pressure from the working volume which, in this case, comprises a vehicle brake. 
     BACKGROUND OF THE INVENTION 
     Such a valve assembly is disclosed in International Patent application no. WO03/031855, and comprises a valve body in which are mounted two pressure responsive pistons, one of which is mounted inside the other, and two return springs, one of which extends between the valve body and the outer piston, and the other of which is located in a chamber inside the outer piston and extends between the outer and inner pistons. An axially extending central aperture is provided through both pistons to allow flow of fluid from a valve assembly inlet into the chamber inside the outer piston and above the inner piston, and into a control chamber above the outer piston. 
     The valve assembly is of relative complex construction, and the parts must be manufactured to a close tolerance to ensure that fluid tight seals can be provided where required whilst allowing the necessary movement of the two pistons, in particular the two pistons must be manufactured to a close tolerance to ensure that a fluid tight seal is provided between the inner and outer pistons whilst allowing relative movement between the two pistons. Moreover, the presence of two return springs in the valve assembly further complicates manufacture of the valve assembly, as one return spring must be inserted into the chamber between the two pistons, and performance of the valve assembly depends partly on the performance of two return springs. In addition, maintenance of the valve assembly is inconvenient because the chamber inside the outer piston in which one of the return springs is located cannot be accessed, for example to check that the seal between the two pistons is adequate and sufficiently well lubricated, or to check or replace the return spring, without dismantling the entire valve assembly. 
     It is specified that the valve assembly described in WO03/031855 is suitable for use as either an ABS or and EBS valve in a vehicle brake system, but this valve assembly is, in fact, more suitable for use as an ABS valve than as an EBS valve. 
     In normal use, an ABS valve is passive and allows flow of fluid from the valve inlet to the vehicle brake, i.e. is in the apply state. Only if wheel lock is detected is the ABS valve assembly activated to either release fluid pressure from the vehicle brake or to hold fluid pressure in the vehicle brake. The valve assembly disclosed in WO03/031855 is in the apply state when the solenoid valve is de-energised. 
     In contrast, an EBS valve assembly must normally be in the release state, i.e. must release fluid from the vehicle brake and block flow of fluid from a pressurised fluid reservoir through the valve inlet. Only when a driver of the vehicle demands braking is the EBS valve assembly operated to allow flow of fluid from the pressurised fluid reservoir to the vehicle brake. The valve assembly disclosed in WO03/031855 is in the release state when the solenoid valve is energised, and therefore electrical power consumption and wear on the solenoid valve would be excessive if this valve assembly were to be used as an EBS valve. 
     SUMMARY OF THE INVENTION 
     According to a first aspect of the invention we provide a valve assembly, the valve assembly comprising a valve body, a first movable pressure responsive element, and a second pressure responsive movable element, the valve body being provided with a first port, a second port and a third port, the first pressure responsive element being moveable into engagement with a first valve seat substantially to block flow of fluid between the second port and the third port, and the second pressure responsive element being movable into engagement with a second valve seat substantially to block flow of fluid between the first port and the second port, wherein the valve assembly further comprises a third movable pressure responsive element which may be moved to engage with the first pressure responsive element and move the first pressure responsive element out of engagement with the first valve seat so that flow of fluid between the second port and the third port is permitted. 
     By virtue of the provision of the third pressure responsive element, the provision of a sealed chamber between the first and second pressure responsive elements, is not required to facilitate movement of the first pressure responsive element with respect to the second pressure responsive element. Thus, construction and maintenance of the valve assembly is simplified. 
     Preferably, the first valve seat is provided on the second pressure responsive element and the second valve seat is provided on the valve body. 
     The valve assembly may be further provided with a resilient biasing element which extends between the valve body and the third pressure responsive element, the third pressure responsive element being configured to be capable of transmitting the biasing force of the resilient biasing element to both the first and second pressure responsive elements. 
     By virtue of the engagement of the resilient biasing element with the third pressure responsive element, the need to provide two separate resilient biasing elements to ensure correct operation of the valve assembly is removed. The valve assembly performance therefore does not depend on the characteristics of two resilient biasing elements. 
     The part may extend through an aperture provided in the second pressure responsive element, there being a substantially fluid tight seal provided between the second pressure responsive element and the third pressure responsive element which allows relative movement of the second pressure responsive element with respect of the third pressure responsive element. 
     The first port is preferably an inlet port, the second port an outlet port, and the third port an exhaust port. 
     The first pressure responsive element may be adapted to move in response to fluid pressure in a control chamber to engage with the first valve seat, and the second pressure responsive element may be adapted to move in response to fluid pressure at the inlet port to engage with the second valve seat. 
     The valve assembly may further comprise a conduit which extends from the inlet port to the control chamber, through a portion of the valve body which is exterior to the first and second pressure responsive elements. Thus the complexity of the first and second pressure responsive elements is reduced, as there is no need to provide an axially extending central aperture through either pressure responsive element in order to direct pressurised fluid from the inlet port to the control chamber. 
     The first pressure responsive element is preferably a diaphragm. Use of a diaphragm rather than a piston and O-ring assembly, reduces frictional energy losses during operation of the valve assembly. 
     Preferably, the valve assembly further comprises a switch valve having a first switch port connected to the inlet port of the valve assembly, a second switch port connected to the control chamber, a third switch port which vents to atmosphere, and a valve member which is movable between a first position in which the third switch port is blocked and flow of fluid from the first switch port to the second switch port is permitted, and a second position in which the first switch port is blocked and flow of fluid from the second switch port to the third switch port is permitted. 
     In this case, the switch valve is preferably electrically operated, supply of electrical power to the switch valve causing movement of the valve member to the first position, and the valve member moving to the second position in the absence of electrical power supply. 
     The switch valve may be a solenoid valve. Alternatively, the switch valve may be a piezoelectric valve. 
     The valve assembly may be suitable for controlling fluid pressure relative to a working volume in three control states, applying, holding or releasing fluid pressure relative to the working volume for example, in which case, the valve assembly may be an EBS valve for a vehicle braking system. 
     According to a second aspect of the invention we provide a vehicle braking system including a source of pressurised fluid, a vehicle brake actuator, and a valve assembly according to the first aspect of the invention, the first port being connected to the source of pressurised fluid, and the second port being connected to the vehicle brake actuator, and the third port venting to a low pressure region. 
     According to a third aspect of the invention we provide a valve assembly comprising an electrically operable switch valve and a main valve for controlling fluid pressure in a working volume in three control states, the main valve having an inlet port, an outlet port and an exhaust port, and the switch valve having a valve member which moves from a first position to a second position in response to supply of an electrical current to the valve, and returns from the second position to the first position following removal of the electrical current, wherein the main valve is configured such that when the valve member is in the first position flow of fluid through the inlet port is substantially prevented and flow of fluid from the outlet port to the exhaust port is permitted, and when the valve member is in the second position flow of fluid from the inlet port to the outlet port is permitted and flow of fluid between the exhaust port and either the inlet or outlet port is substantially prevented. 
     By virtue of this aspect of the invention, the valve assembly may be used as an EBS valve in a vehicle braking system without the need to apply an electrical current to the switch valve in order to maintain the valve assembly in its normal, release state. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       An embodiment of the invention will now be described, by way of example only, with reference to and/or as shown in the accompanying drawings of which: 
         FIG. 1  is a broken away perspective view of a valve assembly according to the invention, 
         FIG. 2  shows the broken away perspective view of  FIG. 1 , the valve being in a) a release state, b) an apply state, and c) hold state, 
         FIG. 3  is a diagrammatic illustration of the valve assembly of  FIG. 1  when in a) a release state, b) an apply state, and c) a hold state, 
         FIG. 4  is a schematic illustration of a vehicle braking system incorporating the valve assembly of  FIG. 1 . 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     Referring now to  FIGS. 1 to 3 , there is shown a valve assembly  10  comprising a valve body  12  in which is provided a first port  14 , a second port  16  and a third port  18 . In this example, the first port  14  is an inlet port, the second port  16  is an outlet port, and the third port  18  is an exhaust chamber which is open to the atmosphere. 
     The valve body  12  has a first cylindrical portion  12   a  and a second cylindrical portion  12   b  of greater diameter than the first cylindrical portion  12   a . The inlet port  14  is provided in an end surface of the first portion  12   a  of the valve body  12  and extends generally axially from the first cylindrical portion  12   a . The outlet port  16  is provided in a cylindrical side wall of the valve body  12  at an interface between the first  12   a  and second  12   b  cylindrical side portions, and extends generally radially outwardly of the valve body  12 . The exhaust chamber  18  is provided in the second cylindrical portion  12   b  of the valve body  12  and includes a plurality of openings through which the exhaust chamber  18  is vented to a low pressure region, in this example to the atmosphere. 
     Mounted within the valve body  12  is a first movable pressure responsive element  20 , which in this example comprises a diaphragm and piston moulding, and a second pressure responsive element  22 , which in this example is a piston. It will be appreciated that both pressure responsive elements could be pistons, but use of a diaphragm is advantageous as it minimises frictional losses during movement of the first pressure responsive element  20  with respect to the valve body  12 . 
     The first pressure responsive element  20  includes a generally circular flexible membrane  20   a  the periphery of which is provided with a thickened rim of generally circular transverse cross-section, a generally circular end plate  20   b  which is mounted generally centrally of the membrane  20   a  and from which extends a generally cylindrical wall portion  20   c.    
     The second portion  12   b  of the valve body  12  is divided into to first  24  and second  26  chambers by means of a partition plate  28 , and the first pressure responsive element  20  is mounted in the first chamber  24  with the rim of the membrane  20   a  located in a groove provided in the periphery of the partition plate  28  and clamped between the partition plate  28  and a locking ring  30  so as to provide a substantially fluid tight seal between the membrane  20   a  and the valve body  12 . The first chamber  24  is adjacent the first portion  12   b  of the valve body  12  and the wall portion  20   c  of the first pressure responsive member extends into the first portion  12   b  of the valve body  12  towards the second pressure responsive element  22 . The partition plate  28  is provided with a generally circular ridge  28   a  which, when the first pressure responsive element  20  engages with the partition plate  28 , surrounds the end plate  20   b , and which provides a support for the membrane  20   a.    
     When the first pressure responsive element  20  moves out of engagement with the partition plate  28 , there is a control chamber  29  between the partition plate  28  and the membrane  20   a  of the first pressure responsive element  20 . 
     An annular sealing ring  32  is mounted in the first chamber  24  of the second portion  12   b  of the valve body  12 , around the wall portion  20   c  of the first pressure responsive element  20 . An O-ring is mounted in an outer surface of the sealing ring  32  and engages with the valve body  12 , and a lip seal is mounted in an inner surface of the sealing ring  32  and engages with the wall portion  20   c  of the first pressure responsive element  20 . The sealing ring  32  thus provides a substantially fluid tight seal between the valve body  12  and the first pressure responsive element. The sealing ring  32  is fixed relative to the valve body  12 , but the lip seal permits the first pressure responsive element  20  to move with respect to the sealing ring  32  whilst providing a substantially fluid tight seal. 
     The membrane  20   a  of the first pressure response element  20  and the sealing ring  32  are arranged such that the exhaust port  18  extends from the valve body  12  between the membrane  20   a  and the sealing ring  32 . The membrane  20   a  and sealing ring  32  thus enclose an exhaust chamber  33 . Apertures are provided in the wall portion  20   c  of the first pressure responsive element  20  adjacent the end plate  20   b , and these provide a conduit for fluid within the wall portion  20   c  to pass into the exhaust chamber  33 . 
     The second pressure responsive element  22  is mounted in the first portion  12   a  of the valve body and comprises a generally annular plate  22   a  from opposite sides of which extend first  22   b  and second  22   c  generally cylindrical tube formations. The first tube formation  22   b  has a smaller diameter than the second  22   c , and extends towards the first pressure responsive element  20  into the space enclosed by the wall portion  20   c  of the first pressure responsive element. The second tube formation  22   c  extends towards the inlet port  14 . The annular plate  22   a , and first  22   b  and second  22   c  tube formations are all arranged coaxially of the valve body  12 . 
     A valve seat formation  34  extends radially inwardly from the first portion  12   a  of the valve body  12 , and provides a generally circular ridge at its inner edge with which the annular plate  22   a  of the second pressure responsive element  22  may engage. In this example, the valve seat formation  34  is separate from the valve body, and an O-ring is used to provide a substantially fluid tight seal between the valve body  12  and the valve seat formation  34 . It should be appreciated, however, that the valve seat formation  34  may be integral with the valve body  12 . 
     The valve seat formation  34  and sealing ring  32  are arranged such that the outlet port  16  extends from between the valve seat formation  34  and sealing ring  32 . The valve seat formation  34  and sealing ring  32  thus enclose a delivery chamber  36 . In addition to the outlet port  16 , there is provided a pressure take off conduit  38  through the valve body  12  from the delivery chamber  36 . The pressure take off conduit  38  extends to pressure sensor  40 , which in this example is mounted on an electronic circuit board of an electronic valve controller  49 , and thus enables the pressure in the delivery chamber  36  to be measured. 
     An inlet chamber  44  is formed between the valve seat formation  34  and the plate  22   a  of the second pressure responsive element  22  and the end plate of the first portion  12   a  of the valve body  12  through which the inlet port  14  extends. 
     The valve assembly further comprises a resilient biasing element  44 , which in this example is a frusto-conical helical compression spring, and a third pressure responsive element  46 , which in this example comprises a rod  46   a  with a generally circular transverse cross section, at one end of which is provided a stop portion  46   b  in the form of a disc of greater diameter than the transverse cross section of the rod  46   a , mounted coaxially of the rod  46   a.    
     The rod  46   a  of the third pressure responsive element  46  has a diameter which is slightly smaller than the internal diameter of the first tube formation  22   b  of the second pressure responsive element  22 , and extends through the space enclosed by the first tube formation  22   b  to engage with the end plate  20   b  of the first pressure responsive element  20 . The stop portion  46   b  has a diameter which is slightly smaller than the internal diameter of the second tube formation  22   c  of the second pressure responsive element  22 , and is located in the space enclosed by the second tube formation  22   c . A sealing element, in this case an O-ring, is located in a groove around an outer edge surface of the stop portion  46   b  and engages with an inner surface of the second tube formation  22   c  to provide a substantially fluid tight seal whilst still permitting movement of the biasing force transmitting rod  46  with respect to the second pressure responsive element  22 . 
     The spring  44  extends from the end plate of the valve body  12  around the inlet port  14  to the stop portion  46   b  of the biasing force transmitting rod  46 . 
     The valve assembly  10  further comprises a switch valve  48 , which in this example is a solenoid valve. The switch valve  48  may, of course, be any other type of electrically operated valve such as a piezoelectric valve, for example. The solenoid valve  48  is located in the second chamber  26  of the second portion  12   b  of the valve body  12  and is provided with three ports and a valve member which is movable under the action of a solenoid between a first and second position. The first port of the solenoid valve  48  is connected to the inlet chamber  42  and thus forms the inlet port, the second port is connected to the control chamber  29  and thus forms the control port, and the third port is vented to a low pressure region, in this example to the atmosphere, and thus forms a solenoid exhaust port. 
     When in the first position, the valve member substantially prevents fluid from passing through the exhaust port whilst permitting fluid to pass between the inlet and control ports, and when in the second position, the valve member substantially prevents flow of fluid through the inlet port whilst permitting fluid to pass between the control and exhaust ports. In this example, the valve  48  is configured such that passage of an electrical current through the solenoid causes the valve member to move to the first position, the valve member returning to the second position on removal of the electrical power supply to the solenoid. 
     An electronic valve controller  49  is provided to control electrical power supply to the solenoid valve  48 , and is typically mounted on the exterior of the valve body  12  adjacent the solenoid valve  48 . The pressure sensor  40  is connected to the electronic valve controller  49 , so that the measured delivery pressure may be fed back to the controller  49  so that the controller  49  may respond appropriately to bring the delivery pressure to a desired valve. 
     Where the inlet port  14  of the valve assembly  10  is connected to a source of pressurised fluid, the valve assembly  10  may be operated to control the fluid pressure in a working volume connected to the outlet port  16  in three control states, namely to apply pressure to the working volume, to hold fluid pressure in the working volume, or to release fluid pressure from the working volume. In this case, the valve assembly  10  operates as follows. 
     As mentioned above, the inlet port  14  is connected to a source of pressurised fluid and thus the inlet chamber  42  is filled with pressurised fluid from that source. The pressure of fluid in the inlet chamber  42  together with the biasing force of the spring  44 , which is transmitted to the second pressure responsive element  22  by engagement of the stop portion  46   b  of the third pressure responsive element  46  with the plate  22   a  of the second pressure responsive element  22 , push the plate  22   a  against the valve seat formation  34  so that fluid flow from the inlet chamber  42  past the valve seat formation  34  is not permitted. If no electrical power is supplied to the solenoid valve  48 , the valve member of the solenoid valve  48  adopts the second position, and thus flow of pressurised fluid from the inlet chamber through the solenoid valve  48  is not permitted. In other words, the valve assembly  10  is acting to block flow of fluid from the source of pressurised fluid. 
     The rod portion  46   a  of the third pressure responsive element  46  engages with the end plate  20   b  of the first pressure responsive element  20  and pushes the end plate  20   b  towards the partition  28 . With the valve member in the second position, flow of fluid through the control and exhaust ports of the solenoid valve  48  is permitted and the control chamber  29  contains fluid at atmospheric pressure. The pressure of fluid in the inlet chamber  42  acting on the stop portion  46   b  of the third pressure responsive element  46  and the biasing force of the spring  44  provide sufficient force that movement of the first pressure responsive element  20  to engage with the partition plate  28  to minimise the volume of the control chamber  29  is not resisted by fluid pressure in the control chamber  29 . 
     The wall portion  20   c  of the first pressure responsive element  20  is of a length such that when the third pressure responsive element  46  pushes the first pressure responsive element  20  to minimise the volume of the control chamber  42 , there is a gap between the wall portion  20   c  of the first pressure responsive element  20  and the plate  22   a  of the second pressure responsive element  22 . Fluid flow from the delivery chamber  36 , and hence the working volume, into the space enclosed by the wall portion  20   c , through the apertures in the wall portion  20   c  into the exhaust chamber  33  is therefore permitted. In other words, there is a path for free flow of fluid between the outlet port  16  and the exhaust port  16  of valve assembly, and thus the valve assembly  10  is acting to release any fluid pressure in the working volume. 
     The valve assembly  10  is thus in the control state in which it releases fluid pressure from the working volume, i.e. release state, as illustrated in  FIGS. 2   a  and  3   a.    
     If electrical power is supplied to the solenoid valve  48 , the valve member moves to the second position, whereby flow of fluid through the exhaust port  48   c  of the solenoid valve  48  is prevented, and flow of pressurised fluid from the inlet chamber  42  to the control chamber  29  is permitted. As fluid pressure in the control chamber  29  increases, the fluid pressure pushes the end plate  20   a  of the first pressure responsive element  20  against the biasing force of the spring  44 . When fluid pressure in the control chamber  42  is sufficiently high to overcome the biasing force of the spring  44 , the first pressure responsive element  20  moves towards the second pressure responsive element  22  until the wall formation  20   c  engages with the plate  22   a  of the second pressure responsive element  22 , thus substantially preventing flow of fluid between the delivery chamber  36  and the exhaust chamber  33 . 
     The area of the end plate  20   b  of the first pressure responsive element  20  is greater than the area of the plate  22   a  of the second pressure responsive element, to that when the fluid pressure in the control chamber  29  is equal to the fluid pressure in the inlet chamber  42  the force exerted on the first pressure responsive element  20  to push the second pressure responsive element  22  away from the valve seat formation  34  is greater than the force acting on the second pressure responsive element  22  to maintain it in contact with the valve seat formation  34 . Thus, when the fluid pressure in the control chamber  42  reaches the same value as the fluid pressure in the inlet chamber  42 , the first pressure responsive element  20  pushes the plate  22   a  of the second pressure responsive element  22  out of engagement with the valve seat formation  34 , thus opening a path for flow of fluid from the inlet chamber  42  into the delivery chamber  36 . Fluid from the source of pressurised fluid may therefore flow through the valve assembly  10  and out of the outlet port  16 . 
     The valve assembly  10  is thus in the control state in which it applies fluid pressure to the working volume, i.e. an apply state, as illustrated in  FIGS. 2   b  and  3   b.    
     The third control state in which fluid pressure in the working volume is maintained, is achieved by applying a fluctuating electrical signal to the solenoid valve  48 . 
     If electrical power to the solenoid valve  48  is switched on and off rapidly, for example at 50 Hz and typically in the range of 25 to 100 Hz, fluid pressure is repeatedly applied to and released from the control chamber  29 . The fluid pressure in the control chamber  29  reaches an equilibrium pressure between atmospheric pressure and the fluid pressure in the inlet chamber  42 . 
     The biasing force of the spring  44  is sufficiently weak that it is overcome by this intermediate control chamber fluid pressure, and thus the first pressure responsive element  20  moves towards the second pressure responsive element  22  until the wall formation  20   c  engages with the plate  22   a  of the second pressure responsive element  22 , thus substantially preventing flow of fluid between the delivery chamber  36  and the exhaust chamber  33 . As the pressure of fluid in the control chamber  29  is lower than the fluid pressure in the inlet chamber  42 , the first pressure responsive element  20  cannot move the second pressure responsive element  22  out of engagement with the valve seat formation  34 , and thus the path for fluid flow from the inlet chamber  42  to the delivery chamber  33  remains substantially closed. 
     The valve assembly  10  is thus in the control state in which it maintains fluid pressure in the working volume, i.e. a hold state, as illustrated in  FIGS. 2   c  and  3   c.    
     The valve assembly  10  may be used as an EBS valve in a vehicle braking system. In this case, the valve assembly  10  is used to supply pressurised fluid to one or more brake actuators  50  to facilitate movement of the vehicle brakes in response to demand for braking from a driver of the vehicle. Such a braking system is illustrated in  FIG. 4 . 
     This braking system comprises four brake actuators  50 , one for each vehicle wheel or set of wheels, and four valve assemblies  10 , the outlet port  16  of each valve assembly  10  being connected to one of the brake actuators  50 . 
     Preferably each valve assembly  10  is mounted adjacent its respective brake actuator  50 , on an exterior surface of the brake actuator  50  housing. The brake actuators  50  are configured such that supply of pressurised fluid from the outlet port  16  of each valve assembly  10  to the actuator  50  causes the brakes to be applied. 
     The braking system further comprises a foot pedal  52  which may be operated by the driver to initiate braking, an electronic central controller  54  which is electrically connected to the foot pedal and to the electronic valve controller  49  of each valve assembly  10 , and a pressurised fluid reservoir  56  which is connected to the inlet ports  14  of each valve assembly  10  and which typically contains compressed air at a pressure of around 8-10 bar. 
     Movement of the foot pedal  52  generates an electrical demand signal, the magnitude of which indicates the degree of braking desired. The demand signal is passed to the central controller  54  which uses a pre-programmed control algorithm to generate an appropriate electrical control signal. The control signal is transferred to each valve controller  49  which supplies an electrical current to the associated solenoid valve  48  to bring the valve assembly  10  into the apply or hold states as described above. 
     The valve assembly  10  described above is particularly suitable for use an EBS valve because the valve assembly  10  is configured to return to the exhaust state, in which no pressurised fluid is supplied to the brake actuator  50 , when no electrical power is supplied to the solenoid valve  48 . 
     It should be appreciated that the valve assembly  10  described above could be used as an ABS valve in a vehicle braking system, although as an ABS valve is normally held in the build state, so that the ABS valve permits fluid pressure generated at the foot pedal to be transferred to the brake actuator  50  to initiate braking, it would normally be necessary to supply electrical power to the solenoid valve  48 . Thus, if the valve assembly  10  described above were to be used as an ABS valve, it would be preferable to effectively reverse the action of the solenoid valve  48 , so that the valve member moves to the second position when energised and returns to the first position when deenergised. 
     Similarly, whilst the valve assembly described in WO03/031855 is particularly suitable for use as an ABS valve, it may be improved for use as an EBS valve, for example in the EBS braking system described above and as shown in  FIG. 4 , by reversing the solenoid valve so that the valve assembly is in the exhaust state when the solenoid is de-energised. 
     When used in this specification and claims, the terms “comprises” and “comprising” and variations thereof mean that the specified features, steps or integers are included. The terms are not to be interpreted to exclude the presence of other features, steps or components. 
     The features disclosed in the foregoing description, or the following claims, or the accompanying drawings, expressed in their specific forms or in terms of a means for performing the disclosed function, or a method or process for attaining the disclosed result, as appropriate, may, separately, or in any combination of such features, be utilised for realising the invention in diverse forms thereof.