IMPROVEMENTS TO PRESSURE PROPORTIONING VALVE

Abstract: In an air pressure proportioning variable load valve for a vehicle compressed air braking system the operating means (12; 58) for a self-lapping valve assembly includes a fluid pressure responsive piston arrangement (18, 19; 48, 50) which is operable above a given fluid pressure (P1) to adjust the pesrton of the self-­ lapping valve arrangement relative to a variable area pressure responsive assembly whereby the rising output pressure corres­ ponds initially to rising input port pressure up to the given pressure (P1) followed by progressive adjustement before prop­ ortioning by virtue of relative areas of the variable area assembly.

Description: Improvements to Pressure Proportioning Valves invention relates to pressure proportioning valves and relates in particular to pressure proportioning valves the characteristics of which produce ouput pressures directly corresponding to input or cntrol pressure up to a predetermined value before giving for higher values of control pressure an output pressure having a variable controllable relationship to the control pressure. Such. proportioning valves are of particular application in the control of vehicle fluid pressure braking systems for controlling braking pressure in accordance with' vehicle load. In tbe Specification of United Kingdom Patent No. 1,585,1G8 there is disclosed a pressure proportioning valve especially for variable load control of braking pressure wherein in order to overcome stiction and return spring resistence in a brake mechanism when a brake application is commenced, the output pressure of the pressure proportioning valve follows a controlling pressure up to a given pressure value before the valve commences to proportion the output in accordance with a load setting. In order to achieve this a pressure responsive member of the proportioning valve is acted upon via an inshot valve with a counteracting pressure up to the given value. Furthermore, the inshot valve is arranged to progressively diminish the inshot pressure through the operating output pressure range. of the proportioning valve so that it does not detrimentally affect the ratio of the proportioning valve more especially for low load settings. An object of the present invention is to provide simpler means for achieving te initial output pressure corresponding to the input pressure up to a pre-determined value before giving an output pressure in accordance with a variable setting. A pressure propositioning valve device including a lapable double valve assembly operating means for the double valve assembly co-operable with a variable area pressure responsive means and a control member therefore said. pressure responsive means being subject to the fluid pressure at a control pressure port in a direction to. tend to open a valve of the assembly, between a pressure source input port and an output port and subject to fluid pressure at the output port in an opposing direction to tend to open a valve of the assembly between the output port and a vent port and characterised by the operating means for the double valve including further fluid pressure responsive means operable above a predetermined pressure corresponding to a given input port pressure value for adjusting the position thereof relative to the variable area pressure responsive means whereat lapping of the double valve can occur towards a position set by the pressure proportioning control member whereby the output port pressure corresponds to the rising input port pressure curve up to said pressure value followed by progressive adjustment before proportioning by virtue of relative areas of the variable area pressure responsive means as set by the control member. order that the invention may be more clearly understood and readily carried into effect, tho same will be further described by way of example with rererence. to the accompanying drawings of which: Fig. 1 illustrates a pressure proportioning valve device in accordance with a f-irst embodiment of the invention .Fig2 illustrates a pressure proportioning valve device in accordance with a second embodiment and, Fig. 3 illustrates an operating characteristic to be referred to Referring to Fig. 1, th.e pressure proportioning valve device shown therein is designed for use as a variable load valve in fluid pressure operable braking systems. The device comprises upper and lower body members denoted by references 1 and 2 respectively, bolted together to clamp the periphery 3 of a variable effective area diaphragm a- central bead 5 of which is retained in a. groove 6 of the skirt of a piston with a seal 35 slideable in a cylindrical bore 8 of the body member 1. The piston 7 carries with it a double valve member 9 which is spring loaded downwards by a spring 10 towards an inlet valve seat 11 formed on an annular flange within the piston. Projecting upwardly towards the double valve member 9 from the region beneath the piston 7 there is a tubular exhaust valve seat member 12 which is sealingly slideable in adore 13 formed within the lower part of the housing. The piston 7 is guided by its seal 35 and a nonsealing guide member 34 and the underside of diaphragm 4 corunicates with an output port 36. Thk lower part of the housing incorporates a dividing wall 14 which separates an output port 15 of the device frmm a vented region 16. The tubular exhaust valve seat 12 has a downwardly extending part 17 between the lower surface of which and a piston 18 there is retained a spring 19. The slideable member 12, the downward extension 17 thereof and luther parts form a fluid pressure responsive operating means for the double valve assembly. The piston 18 slides in a cylinder the lower end 20 of which communicates via a pipe 21 to an input port 22 for the device by which input pressure is applied on top of the piston 7. The piston 18 has an upwardly extending stem 23 the upper surface 24 of which is engageable with a ball-end 25 of a pivotted controlling lever 26 operable through a bearing 27 in the casing by an external. lever 28. The ball-end 25 is trappable between the surface 24 and an internal projection 29 in the exhaust valve member 12. Referring briefly to the variable effective area diaphragm this is of generally well-known form and comprises radially outwardly extending fingers 31 integral with the piston 7 inter-digitating with inwardly extending fingers 32 of an annular member inside the upper body member. The downwardly facing surfaces of fingers 31 and the down wardly facing surfaces of fingers 32 are mutually arranged at an angle whereby upon downward movement of the piston 7 from the position stow, the diaphragm.4 presents- an increasingly effective area to pressure at the output port 15 acting beneath the diaphragm and the region above i.t is vented via an aperture 33. Referring now to the operation of the pressure proportioning valve device with no pressure at the input port 22 and with an unloaded vehicle, the lever 28 is (say) in the position shown aid the valve assembly takes up a positien approximately as shown in Fig. 1, with the piston 18 resting against t'ts stop 34 and with the member 12 against stop 36 by virtue of the spring 19. When input pressure at 22 begins to rise due to operation of a. veh.icle brake valve, after a small pressure increase, the piston 7 is slightly downwardly deflected to cause valve member 9 to seat against 12 unseating the valve member 9 from the seat 11. Input air pressure is thus applied via the unseated valve to the output port 15 and becomes effective on the underside of diaphragm.4. Owing.to the effect of the spring 19, the tubular member 12 is retained over this first part of the characteristic in precisely the position shown regardless of the setting of lever 28, Output pressure therefore initially directly follows input pressure independently of the setting of lever 28 to provide a commencing operating pressure to a brake áctuator up to a pre-determined input pressure at pott 22 as indicated at P1 in Fig. 3. Upon attainment of this pre-determined' downward acting input pressure, at port 22 the exhaust valve member 12 and hence the piston 7 tend to begin to move downwards against the action of spring 19. Simultaneously, the input pressure communicated via pipe 21 to the region 20, acts on tfle underside of piston 18 in a sense to cause it to -i ris -' against the effect of spring 19. This effects an inc ease in, the upward force transmitted to member 12 by spring 19 and tends to prevent downward movement of this me:111 er such that a balanced condition is maintained with noipmovement occurring. As the input pressure continues to rise, however, piston 7, valve member 9 and member 12 gradually move downward and piston 18 continues to rise. In this manner the effective area of diaphragm 4 is progressively increased effecting progressive proportioning of the output pressure. This will continue until at a second pre-determined input pressure indicated at P2 in Fig. 3 the projection 29 of member 12 contacts ball end 25, where upon further downward movement is prevented and the desired proportioning as set by the lever position is attained. At a certain input pressure equal to say P3 which will depend upon the position of ball end 25, stem 23 of piston 18 comes into contact with the lower edges of ball end 25 trapping it between surface 24 and projection 29. This prevents excess stress being transmitted to lever 28 by the nett downward forces transmitted through lever 26 by member 12 is hen input pressures exceed P3. A subsequent reduction of input pressure is represented by tte broken curve of Fig. 3. This causes piston 7 to rise thereby unseating the valve member 9 from the valve seat member 12 at a Ecply pressure port P4 to- commence venting the region beneath diaphragm 4 to exhaust port 16. When the delivered pressure is reduced to a.pprox.imately P2, exhaust valve member 12 begins to rise lifting piston 7 and reducing the effective area of diaphragm 4. This then reduces the degree of brake pressure proportioningachieved until m mber 12 meets the stop 36 on body.;2, whereupon the effective area of diaphragm 4 is at a minimum and the output pressure at port 35 is: equal to the input pressure at port 22. This condition will. then con.tinue until both input pressure and delivery pressure are completely vented. From the foregoing it will be apprecia.ted that by virtue of a pressure responsive means in the form of piston 12, which is responsive to a pre-determined level of input, pressure to modify the position of the piston 7 whereat lapping of the double valve can occur the output port pressure follows the input port pressure up to a. given pressure value before proportioning of the output in relation to the input occurs accordingly to the ad.justable ratio setting for the device. Referring now to Fig. 2, this shows an alternative form of pressure proportioning valve in the form of a device designed to operate as a variable operable relay valve. The evice comprises an upper portion 41 and a lower hou ing portion 41 with an output port 62 communicating with the underside of a diaphragm 43 clamped between the two housing portions similarly to the diaphragm of 1. Concentric with the diaphragm 43 there is carried a,lfkirt 45 of a piston 44 slideable in a cylir.rical bore 46 in the upper part of the housing and an input control port 47 communicating with the upper surface of piston 4. Sealingly slideable within the skirt 45 is a pressure responsive member in the form of a. smaller piston 48 carrying a downwardly projecting exhaust va.lve member 49 which co-operates with a moveable double valve assembly carried in the lower part of the housing. The piston 48 is spring loaded by virtue of "a spring 50 trapped within the piston 45 and the state of compression of which is adjustable by an adjusting screw 51. Furthermore, a vent passage 52 is provided alongside the adjusting screw 51. -The piston 48 and member 49 constitute a pressure responsive operating means for the double valve assembly. Referring now to the double valve assembly, this is carried in a sealingly slideable plunger 53 and comprises a double valve member 5 urged by a light spring 55 towards an input valve seat 56 to which communication is provided via an aperture 57 from an input or reservoir port 58. Although not shown, the plunger 53 has means for adjusting the vertical position of its stem 59 for adjusting the ratio of the valve assembly. In addition, for the purposes of balancing pressures on the self-lapping valve arrange ments, two small passages 60 and 61 are provided whereby the pressure under diaphragm 43 is communicated to the annugus 63 acting upwards on the double valve. In operation of the pressure proportioning relay valve of Fig. 2 and with zero control pressure initially applied at port 47, the double valve is at rest with the lower end/ of 51 against the valve member and the valve member against the inlet valve seat 56. This is so under the influence of springs 50 and 55. When the input pressure begins to rise twits acts on the piston 44 which after overcoming. the force of light spring 55 unseats the valve member from seat 56 thereby allowing air under pressure to be supplied f om the reservoir via port 58 to an output port 62 and to the under-side of¯the diaphragm. Upon attainment.of a pre-determined pressure say 0.7 bar the spring 50 begins to yield to the action. of the pi.ston 48 under the influence of the fluid pressure at the output port and this piston progressively moves with increasing input pressure to its upper stop in piston 44 thereby allowing the diaphragm assembly to move downwards to balance the effects of the input pressure above piston 44 and the output pressure below diaphragm. 43 whereupon the double valve laps with both seats closed off. By virtue of the piston 48 and spring 50 it is. therefore seen that the position of the pressure responsive assembly whereat lapping of the double valve can occur is conditioned upon attainment of the pre-determining pressure whereby the output pressure follows the input pressure up to this value to apply a sufficient working pressure to a brake actuator before the device effects proportioning of the output pressure and the control pressure in accordance withlthe setting of the jdevice by the positioning of the lower plunger 53 and ralve assembly in accordance with vehicle loading. It Will be seen from Fig. 1 and Fig. 2 that alternative embodiments of the invention may readily now be devised herein the device is either a direct pressure proportioning valve device or it a pressure relay device. In addition it will be observed that the pressure corresponding to the control pressure to which the further pressure responsive means responds, Way either be the control pressure iself as in Fig. 1 or, alternatively, it may be the delivered pressurejas in Fig. 2 or even somederivation thereof.

Claims: CLAIMS 1. - A pressure proportioning valve device including a lapal:e double valve assembly (8, 10, 11, 12; 54, 55, 56,49) operating means (12, 25; 52) for the double valve assembly co-operable with a variable area, pressure responsive meats (14, 31,32; 143) and a control member (28; 59) therefore said pressure responsive means being subject to then fluid pressure at a control pressure port (22; 47)- in a directipn to tend to open a valve of the assembly, between a pressure source input port (22; 58) and an output port (36; 62) and subject to fluid pressure at the output port in an opposing direction to tend to open a valve of the assembly between the output port (36; 62) and a vent port (16; 63) and characterised by the opera.ting means (12, 17, 18, 19; 52) for the double valve including futther fluid pressur e responsive means (18 19; 48, 50) operable above a predetermined pressure (P1) corresponding to a given input port pressure value for adjusting the position thereof relative to the variable area pressure responsive means whereat lapping of the double valve can occur towards a position set by the pressure proportioning control member (28; 59) whereby the output port pressure corresponds to the rising input port pressure curve up to said pressure value (P1) followed by progressive adjustment before proportioning by virtue of relative areas of the variable area pressure responsive means as set by the control member (28; 59). 2.' A.pressure proportioning valve device as claimed in claim 1, characterised by the variable area pressure responsive means comprising a fixed area subject te the pressure at the input port and a variable opposing area subject to the pressure at the output port. 3) A pressure proportioning valve device as claimed in claim 2, characterised by the double valve assembly being carried in the variable area pressure responsive means and the operating means for the double valve assembly comprising a vent valve part (12) urged there towards by biassing mean against the action of pressure at the output poSt. 4) f A pressure proportioning valve device as claimed in claim 3 characterised by a pressure responsive piston(18) operable for pressures above the predetermined pressure to overcome the biassing means (19) and to effect coupling between the control member 28 and the operating means (12). 5) A pressure proportioning valve device as claimed in claim 1,, characterised by the double valve assembly (49, 56, 54) being carried in a moveable member (53) and the operating means (48, 49, 50) being carried in the variable area means and comprising a vent valve part (49) carried by a biassed piston (48) moveable in the variable area means under the influence of fluid pressure above the predetermined valve PI at the output port. 6) A pressure proportioning valve device as claimed in claim 5 characterised by the double valve assembly have a passage 57 via which it is supplied with fluid pressure from a port (58) independent of the control pressure port (47). 7) A pressure proportioning valve device as claimed in claims 5 or 6 the moveable member (53) being moveable by the control part (59) relative to the variable area pressure responsive means. I 8) 1 A pressure proportioning valve device as claimed in any ff claims 1 to 7 characterised by means 51 for adjusting any the predetermined pressure. 9) A pressure proportioning valve device substantially as described herein with reference to Fig. 1 or Fig, 2 of the accompanying drawings.

Inventors: JOSEPH, IAN N.
Applicants: BENDIX LIMITED
Application year: 1984
Main classification: B60T8
IPC codes: B60T8