IMPROVEMENTS RELATING TO SELF-LAPPING VALVES AND FLUID PRESSURE SEALS

Abstract: In a self-lapping valve arrangement which responds to a control force or fluid pressure to apply output fluid pressure from a source to a delivery port (3) up to a point where a piston assembly (8, 20) acts in response to the delivered pressure to close off the valve (11, 29) and if said pressure is excessive to open an exhaust path, the piston assembly is provided with an O-ring seal (16) which is located in a groove the flanks (35, 36) of which are of unequal height in order to cause the O-ring to present greater reaction against the cylinder wall for move­ ment in one direction than it does in the other direction thereby reducing or preventing oscillation.

Description: Improvements relating to Self-Lapping Valves and Fluid Pressure Seals This invention relates to self-lapping valves and fluid pressure seals for such valves. Self-lapping valves usually include a double valve arrangement which controls the connection between a delivery port and an exhaust port or a supply port for connection to a source of supply pressure. The double valve is usually controlled by pressure responsive means which acts in one direction in response to a mechanical force or a control signal pressure in a sense to close a passage between the delivery port and the exhaust port and open a passage from the supply port to the delivery port and acts in the opposite direction in response to delivery port pressure in a sense to close off the supply passage and open the exhaust passage. An intermediate, stable lapped condition is usually possible wherein both the said passages are closed. Such valves are commonly employed in wheeled vehicle air braking systems and one problem which can be encountered arises out of oscillation of the pressure responsive means. This is especially likely to occur when a low impedance way through the double valve is provided between the supply port and the delivery port in such a way that the pressure responsive means responds so rapidly to supply port pressure that the pressure responsive means may over-react and overs' + a temporary vent condition between the delivery port and the exhaust port. This causes undesired oscillation, resulting in vibration, noise, wear of components and wasteful loss of air from the source of supply. According to the present invention there is provided a self-lapping valve including. a double valve arrangement which controls the connection between a delivery port and an exhaust port or a port for connection to a source of supply pressure, a pressure responsive means which may be urged in a first direction in response to a force or control fluid pressure in a sense to close a passage from the delivery port to the exhaust port and open a passage from the supply port to the delivery port and which may be urged in a second opposite direction in response to delivery port pressure in a sense to close off the supply passage and open the passage to the exhaust port, said pressure responsive means having means operable to impede its motion and thereby impede oscillation thereof which may otherwise occur. Preferably the means operable to impede the motion of the pressure responsive means is such as to impede its motion in one of said directions rather than in the other of said directions. A preferred means of putting the invention into practice consists of so arranging one or more seals of the pressure responsive means that the pressure responsive means presents an appreciably greater hysteresis in one of its said directions of motion in relation to that in the other of said directions. The invention therefore also provides an annular seal arrangement for a self-lapping valve to act between two relatively movable parts and which comprises a resilient seal member retained in an annular groove of one part and slidable against the other part, said annular groove being of greater depth adjacent one flank of the groove than adjacent the other flank of the groove whereby the resilient seal member exerts different radial forces between said movable parts when urged adjacent the respective one flank or the other flank of the groove. In order that the invention may be more clearly understood and readily carried into effect, the same will be further described by way of example with reference to the accompanying drawing of which Fig. 1 illustrates a dual relay valve for use in controlling a delivery pressure from a tractor braking circuit to a braking circuit of a trailer towed by the tractor and Fig. 2 illustrates on a larger scale the arrangement of a seal of a pressure responsive means employed in the relay valve of Fig. 1. Referring to the drawing, the relay valve of Fig. 1 is intented for use in a dual circuit air pressure braking system for a tractor vehicle which is arranged to tow a trailer. The valve of Fig. 1 is arranged to control the brakes on the trailer in accordance with fluid pressure applied to either or both of two input ports 1 and 2 of the relay valve to control the pressure delivered at the delivery port 3. The pressure at the delivery port 3 is derived from a supply reservoir (not shown) connected ed to a supply port which is out of sight but is in communication with a chamber labelled with the reference 4. The relay valve has a valve housing 6 within which there are two co-axial pressure responsive members in the form of pistons 7 and 8. The region above piston 7 communicates with delivery port 3 and in an aperture 33 the region beneath piston 7 communicates with input port 2 via an aperture 34. The piston 7 has a cylindrical extension 9 which is sealingly slidable in the housing and carries a delivery valve seat 10 against which a sealingly slidable tubular valve member 11 is urged by the effects of a housed spring 12. The valve member 11 is itself sealingly slidable within a tubular exhaust part 13 which extends through a seal 14 to the outside of the housing to communicate with atmosphere through an exhaust port and dirt excluder 15. The piston 8 is subject to pressure at input port 1 via an aperture 30 and is provided with an outer piston seal 16 which will be discussed further with reference to Fig. 2 and a skirt 17 is provided with a further seal 18 of reduced diameter slidable within a reduced diameter cylindrical portion 19 of the housing. Within the piston 8 there is a further slidable piston member 20 the upper surface of which communicates via apertures 21 in the piston 8 with the region above piston 8. The piston member 20 is provided with two ring seals 22 and 23 the space between which communicates with atmosphere via apertures 24 and 25 in the piston 8 and housing respectively. Captive between the piston 8 and the piston member 20 there is a spring 26 which rests on the underside of the piston 8 and on a cup member 27 which is adjustable by a screw 28 by means of a screw-driver gaining access through the central aperture in 13. The screw 28 thereby can be employed to adjust the compression of the spring 26. Downwardly extending from the piston member 20 there is an exhaust valve seat 29 which is engageable with the upper surface of the valve member 11 within the delivery valve seat 10. The valve 11 is thus operable as a double valve. The first circuit of a dual foot valve of a braking system is intended to be connected to the control port 1, the second or parallel circuit is intended to be connected to the port 2 and a coupler for providing a control pressure to a trailer when connected to the tractor vehicle is intended to be connected at the delivery port 3. Furthermore, a reservoir on the trailer is intended to be connected to the region 4. Such a valve is described in BPS No. 1 294 987. Ignoring for the present the operation of the second or parallel brake circuit on the tractor vehicle, if a brake pressure in the first brake circuit is introduced at the port 1 which communicates with the region above the piston 8 via aperture 30, on attainment of a pressure sufficient to compress a spring 32 beneath the piston 8, piston 8 is deflected downwardly to carry the inner piston member 20 and the valve seat 29. During such motion, the valve seat 29 engages the valve member 11, closes off the exhaust passage from the delivery port 3 and unseats the valve member 11 from the delivery valve seat 10 against the effect of the spring 12. Supply pressure in chamber 4 is therefore applied to the delivery port 3 and the underside of the inner piston member 20. When a sufficient pressure is obtained beneath the inner smaller diameter piston member 20, the double valve arrangement laps off at a pressure which is proportional to the pressure acting above the piston member 20 with the addition of a pressure increment corresponding to the effect of the spring 26. It will be understood that in such a lapping off action, the piston 8 remains downwardly deflected and the lapping operation occurs by virtue of sealingly slidable movement of the piston member 20 relative to the piston 8. Spring 26 which gives rise to the said increment provides predominance so that trailer control pressure at 3 is greater than control pressure at 1. When the control pressure at the control port 1 is partially reduced, the piston member 20 first rises in relation to the piston 8 and venting of the delivery port to atmosphere occurs dozen to a pressure at which the control pressure above the piston member 20 again sufficient to re-close the exhaust port. In the case of a fuil reduction to atmosphere of the control pressure at the port 1, the piston member 20 rises under the influence of the delivery pressure at the port 3 until the delivery pressure reaches a value corresponding to the thrust of the spring 26 and thereupon the piston 8 returns upwards under the influence of the spring 32. In order to provide braking of the trailer in the event of failure of the circuit supplying the control port 1, the lower piston 7 is also provided which on the presence of a control port pressure at the port 2 acting beneath it rises to carry the valve assembly 11, 12, 13 upwards to seat the valve member 11 against the exhaust valve seat 29 and further movement causes unseating of the delivery valve seat 10 to provide communication between the chamber 4 and the delivery port. The build up of pressure at the delivery port is communicated via aperture 33 to the region above the piston 7 and at a certain value of the delivery pressure, the valve assembly returns downwardly to enable the double valve to lap. Subsequent reduction of the pressure underneath the piston 7 enables the valve assembly to move downwardly to unseat the valve seat 29 and thereby vent some of the output pressure at port 3 to atmosphere before reclosure and lapping takes place. A complete reduction of the control pressure at 2 to atmospheric pressure results in venting of the delivery port 3 and release of the trailer brakes. In the event of both the circuits 1 and 2 being fully operable, the predominance imposed upon the pressure at the output port 3 by virtue of the present of the spring 26 associated with the upper piston member 20, ensures that the control pressure at the port 2 which is more or less equal to that at the port 1 does not deflect the piston 7 under such conditions. Referring to the operation of the upper piston member 20, assuming that the way through from the supply source at chamber 4 is relatively unimpeded, on separation of the valve member 11 from the delivery valve seat 10, an inrush of pressure into the region beneath the piston member 21 may occur which tends to cause the piston member 20 to over-react such as to move rapidly upwards and by virtue of the presence of the spring 26 between piston member 20 and piston 8, such movement is partially transferred to the piston 8 which thereby tends to bounce. The result of such rapid upward movement of the piston member 20 is therefore an intermittent alternate unseating of the seats 10 and 29 from the valve member 11 with resultant venting of the pressure under the piston member 20. Such oscillation of the piston member 20 together with the piston 8 therefore can result in rapid loss of air from the supply reservoir. In order to reduce the possibility of such oscillation in a valve such as that of Fig. 1 where a low impedance way through for air from supply source to a delivery port is provided, the seal of one or other of the pistons and preferably the outer diameter seal on the piston 8, namely the seal 16 is designed as shown on enlarged scale in Fig. 2. In Fig. 2 it will be seen that the annular groove of the piston 8 has a width which is'somewhat greater than twice the natural diameter of the resilient 0-ring seal 16. The groove is also provided with a depth which varies from the upper flank to the lower flank of the groove such that the depth adjacent the lower flank 56 is approximately half the depth adjacent the upper flank 35. The seal 16 is thus able to move within the annular groove such as to create a reaction between the bottom of the groove and the cylinder wall which is appreciably greater for upward movement of the piston 8 than it is for downward movement of the piston 8. By such means, the piston 8 is thereby designed to have an inherent hysteresis from the point of view of return or upward movement and as such this piston tends to counteract via the spring 26 the tendency for the piston member 20 to oscillate under the influence of inrush of supply air. lhilst the invention has been described more especially in relation to a dual circuit trailer relay valve for a pneumatic braking system, the invention is equally applicable to other forms of relay valve and other forms of seal where it is desirable to provide a seal with a greater hysteresis on movement in one direction than in the other. M1hilst the 0-ring 16 of the seal shown in Fig. 2 is of circular cross-section, the seal may equally be designed to be of rectangular or even wedge shaped configuration. Although in the relay valve of Fig. 1 the invention is applied to a piston seal, the invention might equally be applied to a sealingly slidable stem of a pressure responsive member or other such member which is sealingly movable in a wall. Furthermore whilst the invention is described in the foregoing more particularly in relation to a relay valve, oscillation problems may be encountered in other types of self lapping valve. For example a fluid pressure control valve such as a foot valve which is operable by an applied force via a spring. By applying the invention to a pressure responsive member of such a self-lapping valve such oscillation may equally be prevented or reduced.

Claims: CLAIMS: 1. A self-lapping valve including, a double valve arrangement (10, 11, 29) which controls the connection between a delivery port (3) ann an exhaust port (its) or a port for connection to a soulce of supply pressure eft a pressure responsive moans (8 2c) which may be urged in a first direction in response to a force or control fluid pressure in a sense to close a passage fiom the delivery port to the exhaust <RTI ID=11.19> port and open a passage from the supply port to the delivery port and which may be urged in a second opposite direction in response to delivery port pressure in a sense to close off the supply passage and open the passage to te exhaust port, characterised by said pressure responsive means having means (16, 35, 36) operable to impede its motion and thereby impede oscillation thereof which may otherwise occur. 2. A self-lapping valve as claimed in Claim 1, characterised by the means for impeding motion of the pressure responsive means being arranged to impede motion in one of said directions appreciably more than in the other of said directions. 3. h self-lapping valve as claimed in Claim 2, characterised. by a seal (16) of the pressure responsive means being designed to provide an appreciably greater hysteresis in one of the said directions than in the other of said directions 4. A self-lapping valve as Claimed in Claim 3 cha--acterised by said seal (16) being a piston seal 5 A self-lapping valve as claimed in Claim 4 characterined by the piston seal consisting of an annular groove carrying a resilient seal member and characterised by said groove being of greater depth adjacent one flan (359 of the groove than adjacent the other flank (36) of the groove whereby the resilient seal member (16) exerts different radial forces between the piston and the wall of a cylinder in which it moves when urged towards the respective one flank or the other flank of the groove. 6. A self-lapping valve as claimed in Claim 5 characterised by the flank of greater depth being the flank (35) which in operation is subject to the greatest fluid pressure.

Inventors: AGGETT, BARRY, CORBEN, DAVID, JENNISON, PAUL, NEAL, BRIAN PATRICK, TANNER, DESMOND JOHN
Applicants: BENDIX LIMITED
Application year: 1980
Main classification: B60T15
IPC codes: B60T15, F16J15