referring now to fig1 a compact hydraulic flow control valve 20 according to one embodiment of the present invention is shown . it consists of a solenoid assembly 22 and a body member 24 . body 24 includes a valving mechanism that is constructed of a wave spring 26 , a disc armature 28 and a regulating plunger 30 . fig1 schematically illustrates that energization and de - energization of the solenoid assembly 22 is controlled by control unit 90a . also , valve 20 uses a source of high pressure 44a at its inlet and an outlet to low pressure 48a as well . in fig2 a and 2b , valve 20 is shown mounted to a device such as a vehicle shock absorber 50 having low and high pressure cavities , the flow between which is to be regulated . generally , there is a mounting 32 having a main body 34 . valve 20 may be screwed into mounting 32 or attached in any other suitable manner . valve 20 is sealed into mounting 32 with an o - ring 38 . end cap 42 has inlet ports 40 which are designed to deliver fluid from the high pressure cavity 44 . outlet ports 46 are located in mounting 32 . the main body 52 of member 24 is generally cylindrical and has a central coaxial bore 54 extending between solenoid assembly 22 and end cap 42 . bore 54 has a central land 56 which , along with plunger 30 , defines an upper chamber 31 and a lower chamber 33 . upper chamber 31 is connected to annular space 64 by channels 66 . when valve 20 is mounted as shown in fig2 a and 2b , fluid may freely flow from upper chamber 31 via channels 66 to space 64 and on through outlet port 46 in mounting 32 to the low pressure cavity 48 . undesired fluid leakage between high pressure 44 and low pressure 48 is prevented by o - ring 68 . therefore , the only path for fluid flow between cavities 44 and 48 is from lower chamber 33 to upper chamber 31 via plunger 30 . plunger 30 has a central coaxial bore 58 leading to upper cross - bores 60 which are in fluid communication with upper chamber 31 . beneath bore 58 , and defined by plunger ring 35 , is a cylindrical space 62 . disc armature 28 and plunger 30 operate as a single unit , moving between an upper open position , and a lower closed position shown in fig2 a . wave spring 26 normally biases the plunger 30 to its closed position . when the plunger 30 opens , fluid under pressure flows from chamber 33 to space 62 in a radially inward path , then up through plunger 30 to chamber 31 . movement of plunger 30 is controlled by energization and de - energization of solenoid assembly 22 which creates a magnetic field that pulls armature 28 up toward solenoid 22 against the bias force of spring 28 applied to ledge 23 of plunger 30 by washer 21 . solenoid assembly 22 is mounted above member 24 . assembly 22 consists of a cap 84 having an upper disc - shaped section 82 held in place directly by the upper portion 80 of body 52 . the lower section 88 of cap 84 is cylindrical and has a coil 86 surrounding it . in fig2 a , coil 86 is connected by leads 92 to a pulse generator 90 designed to alternately energize and de - energize coil 86 . upper portion 80 of body 52 and cap 84 hold coil 86 in place along with plate 96 . plate 96 and o - ring 98 seal and protect solenoid assembly 22 from pressurized fluid in upper chamber 31 . another alternate configuration of the present invention is shown in fig4 . the valve 420 still includes a solenoid assembly 422 , a body member 424 , an armature 428 , a wave spring 426 and a regulating plunger 430 . fluid is admitted through ports 440 in end cap 442 . main body 452 has a central bore 454 and a land 456 defining upper chamber 431 and lower chamber 433 . channels 466 permit fluid to exit valve 420 from upper chamber 431 . similar to the configuration of fig2 a , the device of fig4 permits fluid flow when plunger 430 is in its upper open position . the ledge structure detailed in fig3 is incorporated in the structure of fig4 . armature 428 now occupies approximately the same position occupied by lower cap section 88 of fig2 a . consequently , coil 486 generally surrounds armature 428 , thereby still effectively utilizing the magnetic field generated by coil 486 , while further reducing the valve &# 39 ; s size . additionally , spring 426 is located between cap 484 and armature 428 . despite this different position , spring 426 functions essentially the same way as spring 26 to bias plunger 430 downward . the overall operation of the configuration of fig4 is similar to that of the device in fig2 a . the objects of the invention and any other advantages and improvements are readily accomplished by either configuration . fig5 illustrates the most preferred embodiment of the present invention . the solenoid assembly 522 and body member 524 are basically the same as the solenoid assembly 422 and body member 424 of the valve configuration of fig4 . however , the seating arrangement , armature structure and biasing mechanism are different . end cap 542 has inlet ports 540 passing through it to a lower chamber 533 defined by land 556 and plunger 530 . however , end cap 542 now has a frusto - conical indentation 555 with side wall 557 having an inclination of 45 ° to horizontal in the preferred embodiment . the lower portion of plunger 530 is designed to be accommodated by indentation 555 . the lower end of plunger 530 has a bevelled lip 535 forming an angle of 30 ° with the horizontal . when plunger 530 is seated , a line seal is formed with the side wall 557 . when plunger 530 is in its upper position in bore 554 , fluid flows from lower chamber 533 to upper chamber 531 . several advantages are realized with this seating configuration . the machining needed is extremely simple and inexpensive compared to other constructions . the line seal is also less contamination sensitive and less sensitive to viscosity changes , fluid flow forces and turbulence . the conical seating arrangement provides guided seating for repetitive operation . finally , because the sealing diameter and seating diameter are the same , the unseating problem addressed above is not present . plunger 530 is biased downward by a spring 526 which is now located in an upper section 527 of plunger 530 . this construction improves the magnetic performance characteristics of the armature 528 because the outer annular space formerly occupied by springs is now used to enhance the magnetic flux induced by coil 586 . armature 528 has several holes 578 for fluid flow between cap 584 and upper chamber 531 . in the following discussion , it should be kept in mind that the configurations of fig4 and 5 operate in substantially the same manner as the configuration whose operation is now explained with respect to fig1 a , 2b and 3 . where material operational differences do exist , appropriate note will be made . for purposes of this explanation , it will be assumed that the valve is used to alter or otherwise control the damping characteristics of a shock absorber 50 having a high pressure cavity 44 , and a low pressure cavity 48 designed to accept fluid during compression . fig2 a and 2b show such a mounting configuration . normally , plunger 30 is biased closed , i . e . plunger ring 35 is in sealing contact with end cap 42 , thereby preventing fluid flow from cavity 44 to cavity 48 . likewise , in fig5 the line seal between plunger 530 and side wall 557 is in place . if solenoid assembly 22 remains de - energized during compression of the shock absorber 50 , the damping characteristics of shock absorber 50 are maintained without alteration . to ensure there is no seepage of pressurized fluid under plunger ring 35 , a special structure shown in detail in fig3 is used . as seen in fig3 in some embodiments , the outer edge of ring 35 is radially outside the outer surface 73 of plunger 30 . this radial difference is represented in fig3 by arrow 74 . the high pressure in lower chamber 33 induces a certain amount of pressure downwardly on ledge 23 , as depicted by arrows 72 . this downward pressure on ledge 23 is specifically designed to counter the aggregate force existing between ring 35 and cap 42 as a result of the pressure difference between chamber 33 and space 62 ( in which the pressure tends to approximate 0 psi ). the aggregate resulting upward pressure is represented by arrows 70 in fig3 . thus , applicant has utilized the high pressure in chamber 33 which can cause unseating of the plunger 30 if the resulting upward pressure 70 is greater than the biasing force of wave spring 26 , and has created an additional downward biasing force 72 so that plunger 30 remains down unless the solenoid 22 is energized . the bottom ring configuration 35 of plunger 30 and the seating arrangement of fig5 permit the greatest fluid flow possible with the least vertical movement of armature 28 . in this way , a large flow of pressurized fluid ( to decrease damping of shock absorber 50 ) is achieved while minimizing the space and response time needed in valve 20 for armature 28 and plunger 30 to open . when the damping of shock absorber 50 is to be decreased , solenoid assembly 22 is modulated to allow fluid flow in a predetermined fashion . the coil 86 and other elements of solenoid assembly 22 create an improved magnetic circuit . the coil shape and its proximity to armature 28 yield a greater motive force with less current than earlier devices . there is also considerably less magnetic flux leakage than in earlier devices . this is important because one of the primary objects of this valve is to achieve the fastest response time possible between solenoid energization and armature / plunger movement . armature 28 is also specially designed to accomplish maximum efficiency and fast response times . one or more holes 78 are drilled through armature 28 for several reasons . first , holes 78 reduce any suction or adhesion impeding or delaying movement of armature 28 away from plate 96 when solenoid 22 is de - energized . further , holes 78 reduce the weight of armature 28 , and therefore momentum and inertia , to increase response time . finally , holes 78 provide additional flow paths for fluid being displaced during movement of armature 28 in either direction . plunger 30 ( with ring 35 or side wall 557 ) and armature 28 ( in conjunction with solenoid 22 ) are therefore designed with two goals in mind -- minimize the size of the valve while enhancing the response time . response time is improved by one other feature . a number of notches 76 surround the surface 73 of plunger 30 as shown in fig3 . notches 76 provide hydraulic balancing forces to keep plunger 30 centered in bore 54 . without these balancing forces , hydraulic forces would push plunger 30 horizontally against the wall of bore 54 , thereby holding plunger 30 statically in bore 54 . while some minimal leakage can occur , it is insignificant with respect to the valve &# 39 ; s efficient operation . when solenoid 22 is modulated , a controlled flow travel path for pressurized fluid is provided . armature 28 is magnetically reciprocated , moving plunger 30 between its open and closed positions rapidly . this movement is rapid and covers only a very short distance ; but the disc valve and annular opening configuration of ring 35 and cap 42 and the conical side wall 557 and bevelled plunger lip 535 mean that appreciable flow rates can nevertheless be achieved . modulation of solenoid 22 can be controlled by a variety of devices -- a microprocessor , analog controls , and others . other variations , modifications and applications will become apparent to those skilled in the art . in particular , a number of other applications of the valve are possible . any device or system having size restrictions and requiring high response characteristics in a regulating valve would benefit from incorporating the valve . therefore , the above description of the preferred embodiments is to be viewed as illustrative rather than limiting . the scope of the present invention is limited only by the scope of the claims that follow .