Pressure regulating valve assembly for a hydraulic damper

Abstract: A pressure regulating valve assembly (100) includes a valve body (102) mounting an electric solenoid assembly (189). The solenoid assembly controls the fluid pressure in a pilot pressure chamber (142) defined in the valve body. Fluid in the pilot pressure chamber is biased against a deflectable disc (162) which controls fluid flow through the pressure regulating valve assembly. Control of electric current to the solenoid assembly controls fluid pressure in the pilot pressure chamber and, thus, fluid flow through the pressure regulating valve assembly. When utilized with a hydraulic damper and a controller, the present pressure regulating valve assembly provides continuously variable damping in real time.

Description: The present invention relates generally to an electrically controlled hydraulic damper for a vehicular suspension system. In particular, the present invention is concerned with an (electro-hydraulic) pressure regulating valve assembly for continuously varying a damping force in real time for semi-active ride control. Electrically controlled hydraulic dampers (shock absorbers and struts) for vehicular suspension systems are well-known. Many controllable shock absorbers utilize an electric solenoid or motor-driven member to select different damping characteristics. Due to small electric actuators and the high friction of the movable members, many known controllable dampers are limited in response time, and are not suitable for real time systems. A particular damping setting, once selected, cannot be changed quickly enough to respond to the next individual suspension movement. In addition, many devices select from a limited group of discrete settings and are not capable of providing continuously variable damping. The art continues to seek improvements. It is desirable to provide a continuously variable hydraulic damper capable of real time response. Examples of the prior art can be found in US-A-4,902,034; and US-A-4,785,920. A pressure regulating valve assembly in accordance with the preamble of claim 1 is disclosed in GB-A-2164723. A pressure regulating valve assembly in accordance with the present invention is characterised over GB-A-2164723 by the features specified in the characterising portion of claim 1. The present invention includes a pressure regulating valve assembly, particularly suited for use with a hydraulic damper. The pressure regulating valve assembly permits a hydraulic damper to provide continuously variable damping in real time through a computer controller. Fluid pressure in the pressure regulating valve assembly is proportional to electric current supplied to a solenoid coil. Each electrical signal inputted to the solenoid assembly produces a specific pressure output independent of fluid flow to the pressure regulating valve assembly. An armature in the pressure regulating valve assembly shifts in response to varying fluid flow to maintain the output pressure. The present, compact valve assembly is suitable for mass production and use on passenger and commercial vehicles. In a preferred embodiment, the present pressure regulating valve assembly includes a valve body mounting an electric solenoid assembly. The solenoid assembly controls the fluid pressure in a pilot pressure chamber defined in the valve body. Fluid in the pilot pressure chamber is biased against a deflectable disc which controls fluid flow through the pressure regulating valve assembly. Control of electric current to the solenoid assembly controls fluid pressure in the pilot pressure chamber and, thus, fluid flow through the pressure regulating valve assembly. When utilized with a hydraulic damper and a controller, the present pressure regulating valve assembly provides continuously variable damping in real time. The present invention will now be described, by way of example, with reference to the accompanying drawings, in which:- Figure 1 is a longitudinal sectional view of a hydraulic damper having an (electro-hydraulic) pressure regulating valve assembly according to the present invention; Figure 2 is a greatly enlarged longitudinal sectional view of the pressure regulating valve assembly of Figure 1 removed from the hydraulic damper; and Figure 3 is an exploded sectional view of a portion of the pressure regulating valve assembly of Figure 2. A hydraulic damper is indicated generally at 10 in Figure 1. The hydraulic damper 10 includes an (outer) reservoir tube 12 defining a support struture which is closed at its lower end by an end cap 14. A bracket 16 is provided about a lower portion of the reservoir tube 12 for securing the hydraulic damper 10 to a vehicular road wheel assembly (not illustrated) in a well-known manner. A seal cover 18 is welded or otherwise secured to the upper end of the reservoir tube 12. A (fluid-filled) inner cylinder 20 is spaced inwardly from and concentric with the reservoir tube 12. The interior volume between the inner cylinder 20 and the reservoir tube 12 forms a fluid reservoir 22. A piston 24 is slidably mounted inside the inner cylinder 20 and divides the interior volume of the inner cylinder 20 into an upper chamber 26 and a lower chamber 28. The piston 24 includes internal valving (not illustrated) which permits only one-way flow from the lower chamber 28 to the upper chamber 26 as the piston 24 reciprocates in the inner cylinder 20. A compression valve assembly 30 secured to the lower end of the inner cylinder 20 controls the one-way flow of fluid from the fluid reservoir 22 into the lower chamber 28 during operation of the hydraulic damper 10 as described below. A piston rod 32 is attached at its inner end to the piston 24 and is connected at its upper end (not shown) to bodywork of a vehicle in any conventional manner. The piston rod 32 passes through a rod guide 34 mounted at the upper end of the inner cylinder 20 and held in position by the seal cover 18. An annular elastomeric seal (not illustrated) is seated on the rod guide 34 and has sealing contact with the piston rod 32 to prevent loss of hydraulic fluid from the upper chamber 26 as the piston 24 strokes in the inner cylinder 20 during operations. A (tubular) sleeve insert 36 is fitted between the inner cylinder 20 and the reservoir tube 12 near the lower end of the inner cylinder 20. The sleeve insert 36 includes a plurality of radially, spaced-apart ribs 38 on its outer surface which produce an interference fit against the reservoir tube 12. A pair of annular flanges 40,42 provided on the inner surface of the sleeve insert 36 support a sealing ring 44 which provides a fluid seal against the inner cylinder 20. An undercut 46 in the upper end of the sleeve insert 36 forms an annular seat 48 for receiving a lower end of an intermediate tube 50 concentrically mounted between the inner cylinder 20 and the reservoir tube 12. The upper end of the intermediate tube 50 is mounted on the rod guide 34. If desired, an annular spacer 52 can be provided between the intermediate tube 50 and the seal cover 18. An annular fluid port 54 is provided in the rod guide 34 to permit fluid to pass from the upper chamber 26 to a bypass channel 56 formed in the annular space between the inner cylinder 20 and the intermediate tube 50. The bypass channel 56 is in fluid communication with an annular fluid receiving chamber 58 formed between the inner cylinder 20 and the sleeve insert 36. A (tubular) adapter 60 having internal threads is received in complementary openings 62,64 in the bracket 16 and the reservoir tube 12 and is sealingly secured to the sleeve insert 36 by any suitable means. A plurality of radial channels 66 are provided in the adapter 60 which are in fluid communication with the fluid reservoir 22. As described below, a (continuously variable electro-hydraulic) pressure regulating valve assembly indicated generally at 100 is threaded to the adapter 60. The pressure regulating valve assembly 100 changes the damping force provided by the hydraulic damper 10 by permitting fluid to flow from the bypass channel 56 to the fluid reservoir 22 as described below. The valve assembly 100, illustrated best in Figures 2 and 3, includes a generally tubular valve body 102 having an outer wall 104 threaded at its central portion 106. The threaded central portion 106 of the outer wall 104 is received by the internal threads of the adapter 60 as described above. The outer wall 104 has a pair of axially spaced annular flanges 108,110 formed between the threaded central portion 106 and an outer end 112 of the valve body 102. A seal ring 114 is positioned around the outer wall 104 axially inwardly from the flange 108 to prevent escape of fluid across the threaded connection between the adapter 60 and the valve body 102. The interior of the valve body 102 includes a (small diameter) cylindrical wall 116 and a (large diameter) cylindrical wall 118. An annular seat 119 is formed at the intersection of the cylindrical walls 116,118. An undercut 120 is formed in the (small diameter) cylindrical wall 116 which intersects a plurality of (radially spaced) ports 122 (port means) passing through the outer wall 104. An internally threaded portion 124 is provided in the (small diameter) cylindrical wall 116 between the undercut 120 and an inner end 126 of the valve body 102. A (small diameter) return channel 128 is provided in the valve body 102 radially outbound of the (small diameter) cylindrical wall 116 between the annular seat 119 and the undercut 120. If desired, flow restrictors (not illustrated) can be mounted in the return channel 128. A groove 130 is formed in the outer wall 104 between the ports 122 and the inner end 126 of the valve body 102. A seal ring 132 is retained in the groove 130 and provides a fluid seal against the adapter 60. A centre pole 134 has a central body 136, a short extension 138 projecting from one end of the central body 136, and a long extension 140 projecting from the opposite end of the central body 136. The outer diameter of the central body 136 is complementary to and received in the (small diameter) cylindrical wall 116 of the valve body 102. A pilot pressure or fluid chamber 142 is formed as a longitudinal channel along the axis of the centre pole 134. An internal cavity 144 having a diameter greater than the pilot pressure chamber 142 is formed in the short extension 138 and connected to the pilot pressure chamber 142 by an annular shoulder 146. An internal cavity 148 having a diameter greater than the pilot pressure chamber 142 is formed in the long extension 140. A tubular, hardened insert 150 is press-fitted into the internal cavity 148 and preferably protrudes slightly beyond the long extension 140. An annular depression 152 is formed in an end of the central body 136 which encircles the short extension 138. An undercut 154 is formed in the outer circumference of the short extension 138 adjacent the central body 136 to form an annular seat 156. Preferably, the remainder of the outer circumference of the short extension 138 is threaded as illustrated in the Figures 2 and 3. A plurality of angled spur channels 158 provide fluid communication between the pilot pressure chamber 142 and the annular depression 152. A disc and seal assembly 160 includes a flexible disc 162 (deflectable disc means) and a reinforced seal 164. Preferably, the reinforced seal 164 is affixed to the flexible disc 162 by any suitable means, including an adhesive. The flexible disc 162 is flexible in response to axial fluid motion described below. The reinforced seal 164 is a cup-shaped rubber element having an annular, curved flange 166 and preferably reinforced with a stainless steel mesh 167. As described below, the flange 166 forms a dynamic face seal against the periphery of an inner wall of the annular depression 152 as the flexible disc 162 deflects. The disc and seal assembly 160 is received over the short extension 138 through respective openings so that the flexible disc 162 rests on the annular seat 156. The flange 166 of the reinforced seal 164 is fitted into the annular depression 152 and the flexible disc 162 is fitted within the inner cylindrical wall of the annular depression 152. A valve nut 168 retains the disc and seal assembly 160 on the centre pole 134. The valve nut 168 is a cylindrical element having a central opening 170 in a hub 171 and a plurality of fluid ports 172 surrounding the hub 171. An annular, raised seat 173 is provided on a surface of the valve nut 168 facing the disc and seal assembly 160 radially outbound of the fluid ports 172. Internal threads 174 are provided on an inner cylindrical wall of the central opening 170 and external threads 176 are provided about the circumference of the valve nut 168. The internal threads 174 are mated with the external threads of the short extension 138. Simultaneously, external threads 176 are mated with the internal threads 124 of the (small diameter) cylindrical wall 116 of the valve body 102. When the valve nut 168 is threaded onto the short extension 138, the flexible disc 162 rests against the seat 173 to inhibit fluid flow through the fluid ports 172 as the seal and disc assembly 160 is clamped between the annular seat 156 and the valve nut 168. A (cup-shaped) restrictor 178 is press fitted into the cavity 144 provided in the short extension 138. The restrictor 178 includes a small diameter opening or pilot orifice 180 to permit fluid to pass into the pilot pressure chamber 142 as described below and thereby define flow restrictor means. A (small cylindrical) retainer 182 is press-fitted over the hub 171 of the valve nut 168 to secure a low flow filter 184. A (large cylindrical) retainer 186 is press-fitted over the inner end 126 of the valve body 102 to secure a high flow filter 188. The high flow filter 188 screens fluid entering the fluid ports 172 and the central opening 170 of the hub 171, while the low flow filter 184 screens only fluid entering the central opening 170. The filters 184,188 can be formed from any suitable material, including phosphor-bronze screen. An electric solenoid assembly (solenoid controlled valve means) 189 is mounted on the long extension 140 of the centre pole 134 and is received in the (large diameter) cylindrical wall 118 of the valve body 102. The solenoid assembly 189 includes a (tubular) bobbin 190 having an axial opening for receiving the long extension 140. Terminal pins 192 (only one of which is illustrated in Figure 2) are pressed into the bobbin 190 prior to the winding of a coil 194 on the bobbin 190. Lead wires 196 are crimped to the terminal pins 192 and extend to an electric controller (not illustrated). A (cup-shaped) ring pole 198 is inserted over the bobbin 190 and coil 194. A (non-conductive) encapulant 199 is provided about the coil 194 and ring pole 198 and the lead wires 196 to a position beyond the valve body 102. A hinged or tapered armature 200 is positioned within a non-magnetic ring spacer 202 so that the hinged armature 200 rests on an outer end of the hardened insert 150. An armature plate 204 is captured between the ring spacer 202 and an end cap 206 and limits the range of movement of the tapered armature 200 as described below. The very small range of travel between the hinged armature 200 and the armature plate 204 provides real time pressure change in the pilot pressure chamber 142 in response to electrical signals to the coil 194. A flange 208 on the end cap 206 is crimped onto the outer annular flange 110 of the valve body 102 to retain the solenoid assembly 189. A pair of seal rings 210,212 are provided about the solenoid assembly 189 to prevent fluid leaks from the valve body 102. In operation, the piston 24 and piston rod 32 reciprocate inside the inner cylinder 20 in a well-known manner. Fluid in the upper chamber 26 is directed by fluid ports 54 to the bypass channel 56 and fluid receiving chamber 58. At this point, fluid at a supply pressure passes through filters 188,184 and enters the (electro-hydraulic) pressure regulating valve assembly 100 described above. The majority of fluid (the main flow) that enters the pressure regulating valve assembly 100 passes through the fluid ports 172 of the valve nut 168 and deflects the flexible disc 162 away from the valve nut 168. The reinforced seal 164 prevents fluid leakage around the perimeter of the deflected flexible disc 162. When the flexible disc 162 is deflected, fluid passes through the ports 122 in the valve body 102 and the radial channels 66 of the adapter 60 to enter the fluid reservoir 22. From the fluid reservoir 22, fluid returns to the lower chamber 28 through the compression valve assembly 30 in a well-known manner. The solenoid assembly 189 is used to control fluid pressure in the pilot pressure chamber 142 and, therefore, the deflection of the flexible disc 162 and fluid flow past it. A small amount of fluid (the pilot flow) entering the pressure regulating valve assembly 100 passes through the pilot orifice 180 in the restrictor 178 to reach the pilot pressure chamber 142. This pilot flow remains substantially constant into the pilot pressure chamber 142. When the solenoid assembly 189 is not energized, pressure in the pilot pressure chamber 142 reaches a sufficient level to cause the tapered armature 200 to be unseated from the hardened insert 150. Fluid flows from the interior of the end cap 206 to the return channel 128 to ports 122 and radial channels 66 to return to the fluid reservoir 22. When the solenoid assembly 189 is energized, the tapered armature 200 is pulled toward the hardened insert 150, restricting pilot flow from exiting through the insert 150 and increasing pressure in the pilot pressure chamber 142. Increased fluid pressure in the pilot pressure chamber 142 and spur channels 158 resists the deflection of the flexible disc 162 as fluid presses against the (cup-shaped) reinforced seal 164, resulting in an increase in fluid pressure in the hydraulic damper 10. In this manner, the amount of electrical current applied to the solenoid assembly 189 can continuously vary the damping of the hydraulic damper 10. A hydraulic damper 10 according to the present invention can be installed at each wheel assembly of a vehicle. An electronic controller can receive various inputs from accelerometers and position sensors along with vehicle speed, brake status and steering position. A control algorithm determines an optimal damping force and energizes the respective solenoid assemblies 189 to change the fluid pressures in the hydraulic dampers. Each corner can be independently changed to provide a desired damping.

Claims: A pressure regulating valve assembly (100) for disposition on a support structure (12), comprising a valve body (102) disposable on the support structure; a fluid chamber (142) provided in the valve body; electric solenoid-controlled valve means (189) for controlling the pressure of fluid in the fluid chamber; port means (122) in the valve body capable of routing fluid from a source of fluid (58) at a supply pressure to a fluid reservoir (22); and deflectable disc means (162) for controlling the flow of fluid through the port means, wherein the deflectable disc means is in fluid communication with the fluid chamber so that pressure in the fluid chamber opposes the deflection of the deflectable disc means; characterised in that an inner end of the valve body (102) is capable of fluid communication with the source of fluid (58); and by flow restrictor means (178,180) for providing a pilot flow of fluid from the source of fluid to the fluid chamber. A pressure regulating valve assembly as claimed in claim 1, including seal means (164) on the deflectable disc means (162) for preventing fluid leakage from the fluid chamber (142) to the fluid reservoir (22). A pressure regulating valve assembly as claimed in claim 2, wherein the seal means comprises a cup-shaped elastomeric element (164) affixed to the deflectable disc means (162). A pressure regulating valve assembly as claimed in claim 3, wherein the cup-shaped elastomeric element (164) is reinforced. A pressure regulating valve assembly as claimed in any one of claims 1 to 4, wherein the solenoid-controlled valve means (189) includes a tapered armature (200) for controlling fluid exiting the fluid chamber (142) to the fluid reservoir (22). A pressure regulating valve assembly as claimed in any one of claims 1 to 5, wherein the fluid chamber (142) is formed as a channel in a centre pole (134). A pressure regulating valve assembly as claimed in claim 6, including a hardened insert (150) in the fluid channel (142) to provide a stop for the solenoid-controlled valve means (189). A hydraulic damper for a suspension system comprising a reservoir tube (12) securable to a wheel assembly; an inner cylinder (20) concentrically mounted in the reservoir tube and which is fluid filled; a fluid reservoir (22) formed in the interior volume between the inner cylinder and the reservoir tube; a piston (24), reciprocally mounted in the inner cylinder, secured to a piston rod (32) extending through an upper end (18) of the inner cylinder and dividing the interior of the inner cylinder into upper and lower chambers (26,28); piston valve means for controlling the flow of fluid from the lower chamber to the upper chamber as the piston reciprocates; compression valve means (30) for controlling the flow of fluid from the fluid reservoir to the lower chamber as the piston reciprocates; bypass channel means (56) for receiving fluid from the upper chamber as the piston reciprocates; and a pressure regulating valve assembly (100) as claimed in claim 1 for controlling the flow of fluid from the bypass channel means to the fluid reservoir; wherein the bypass channel means provides the source of fluid for the pressure regulating valve assembly.

Inventors: CASCIO EUGENE JOHN JR, FORTON DONALD EUGENE, MAGURAN GENE ALLEN JR, SPAKOWSKI JOSEPH GEORGE, STOLTMAN DONALD DIBBLE, CASCIO, EUGENE JOHN, JR., FORTON, DONALD EUGENE, MAGURAN, GENE ALLEN, JR., SPAKOWSKI, JOSEPH GEORGE, STOLTMAN, DONALD DIBBLE
Applicants: GEN MOTORS CORP, GENERAL MOTORS CORPORATION
Application year: 1992
Main classification: F16F9
IPC codes: F16F9, G05D16