Title of Invention	A DIRECTLY OPERATED PNEUMATIC VALVE ASSEMBLY
Abstract	The invention relates to a directly operated valve assembly comprising a valve body having a pressurized air supply inlet port in communication with a source of pressurized air, and at least one cylinder port; a valve bore extending axially within said valve body; a valve member supported within said valve bore and positionable only betrween a first position and a predetermined second position within said valve bore to selectively direct pressurized air from said inlet port through said at least one cylinder port in said second position, said valve member comprising a pair of opposed valve heads, at least one of said opposed valve heads having a recess; an actuator mounted to said valve body for moving said valve member in a first direction to said second position and a biasing member disposed within said recess between said valve member and said valve body adapted to provide a biasing force to said valve member in an opposite second direction to move said valve member to said first position; and an air—assist passage providing a source of pneumatic pressure that acts in combination with said

Title of Invention

A DIRECTLY OPERATED PNEUMATIC VALVE ASSEMBLY

Abstract

The invention relates to a directly operated valve assembly comprising a valve body having a pressurized air supply inlet port in communication with a source of pressurized air, and at least one cylinder port; a valve bore extending axially within said valve body; a valve member supported within said valve bore and positionable only betrween a first position and a predetermined second position within said valve bore to selectively direct pressurized air from said inlet port through said at least one cylinder port in said second position, said valve member comprising a pair of opposed valve heads, at least one of said opposed valve heads having a recess; an actuator mounted to said valve body for moving said valve member in a first direction to said second position and a biasing member disposed within said recess between said valve member and said valve body adapted to provide a biasing force to said valve member in an opposite second direction to move said valve member to said first position; and an air—assist passage providing a source of pneumatic pressure that acts in combination with said

Full Text	DIRECTLY OPERATED PNEUMATIC VALVE HAVING AN AIR ASSIST RETURN BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The invention relates, generally, to pneumatic valve assemblies and, more specifically, to a directly operated pneumatic valve having an air assist return. 2. Description of the Related Art [0002] Directly operated, or actuated, pneumatic valves are well known in the art for controlling the flow of pressurized air therethrough. Directly operated valves may be used alone or in connection with, for example, spool valves and regulators that, in turn, control the flow of pressurized air to and from various pneumatically actuated devices such as press clutches, air brakes, air cylinders or any other pneumatic device or application requiring precise control of operating air. More specifically, two-way, three-way and four-way direct operated valve assemblies are commonly employed in these environments. Such valves typically include a valve body having a valve bore formed in the valve body. A valve member is movably supported within the valve bore from one position to another in direct response to an operative force placed on the valve member by an actuator. A plurality of ports are used to connect the valve assembly to a system supply pressure as well as the various active devices that the valve may control. The actuator is typically an electromagnetically operated solenoid that is energized to move the valve member to a predetermined position within the valve bore. A return spring is often employed to bias the valve member back to a known non-energized position. Valves of this type are employed in a wide variety of manufacturing environments where a high flow rate and very fast response time are desired. [0003] As the technology for these valves has advanced, there has been an increase in the demand for smaller valves that are designed to be employed in operating environments with ever decreasing physical dimensions. In addition, the advance in technology has dictated that the valves must be able to operate with very fast cycle times. In fact, the demand for greater speed and shorter response time is an ongoing requirement for valves of this type. However, in the past, certain design barriers have limited the extent to which the size of the valve assembly could be reduced while at the same time increasing its speed. When the valve member and the valve bore are reduced below a predetermined size, the return spring may be of insufficient physical size and mechanical strength to overcome the inertia of the valve member. In addition, after the valve member has been biased in one direction by the actuator, frictional forces and surface adhesion can build up at the interface of the valve member seals and the valve bore. These frictional forces and related surface adhesion can act to inhibit movement of the valve member in the opposite direction and reduce valve speed and therefore increase valve response time. In this case, the return spring may be unable to provide enough biasing force to quickly or effectively move the valve member from its energized position and return it to the non-energized position when the actuator force is removed. When this occurs, accurate control of the active device is lost. To counter this shortcoming, various design strategies have emerged. However, the design strategies that have been proposed in the related art all suffer from the disadvantage that they add supplemental mechanisms, hardware, or require a remote mounting of the valve. [0004] For example, one design strategy proposed in the related art involves the use of dual electromagnetic actuators to move the valve member in opposite directions. Thus, the return spring is replaced by an electromagnetic actuator such as a solenoid. Unfortunately, this solution adds the complexity of a second solenoid and its associated parts, and also creates another size limiting boundary. On the other hand, single electromagnetic actuators that energize in both directions have been suggested in the related art. However, these single electromagnetic actuators require a bulkier double wound actuator as well as additional electronic circuitry and controls. Thus, directly operated valves that employ the bulkier single electromagnetic operators are typically mounted in a remote location relative to the pneumatically actuated device they control. Unfortunately, the remotely located valves defeat the purpose of smaller, lighter, and more accurate valve designs that can be mounted in very close proximity to the active devices. Also, they must be interconnected via conduits or other flow passages, which require additional hardware and plumbing, and can lower pneumatic efficiencies and introduce line losses within the system. [0005] While the use of the larger conventional valves, either remotely disposed or with the addition of other components, has generally worked for their intended purposes, there remains an ongoing need in the art to simplify pneumatic systems and thereby lower costs of manufacture and/or assembly by creating ever smaller, yet highly accurate, fast actuating, directly operated pneumatic valves. Smaller directly operated valves can be located in very close proximity to active system components, thereby shortening flow paths, reducing or eliminating additional plumbing and hardware, and increasing pneumatic flow efficiency. Unfortunately, the design strategies that have been proposed in the related art have failed to overcome the problems created when the valve member and bore are reduced in size past the point where a return spring has the physical size and mechanical force to quickly, effectively, and repeatedly return the valve member of a fast acting valve to the non-energized position. SUMMARY OF THE INVENTION [0006] The present invention overcomes these design barriers and other disadvantages of the related art in a directly operated valve assembly. More specifically, the present invention is directed toward a directly operated valve assembly including a valve body having a pressurized air supply inlet port in communication with a source of pressurized air, and at least one cylinder port. A valve bore extends axially within the valve body, and a valve member is moveably supported within the valve bore between predetermined positions to selectively direct pressurized air from the inlet port through the cylinder port. An actuator is mounted to the valve body for moving the valve member in a first direction and a biasing member is disposed between the valve member and the valve body to provide a biasing force to the valve member in an opposite direction. Also, an air-assist passage is included for providing a source of pneumatic pressure that acts in combination with the biasing member to operatively move the valve member in a direction opposite to the movement induced by the actuator. r00071 The directly operated valve assembly of the present invention has distinct advantages over the valves known in the related art. The air-assist passage provides a source of pneumatic pressure from the pressurized cylinder port that acts in combination with the biasing member to operatively move the valve member in a direction opposite to the movement induced by the actuator. Importantly, the air assist facilitates a faster acting valve. More specifically, valve assemblies employing the air assist of the present invention may include a smaller biasing member that generates less force than would be required without the air assist. Because the biasing member generates less force, the actuator has less force to overcome and therefore moves the valve member to its first position faster. In addition, the biasing member, along with the air assist provided through the passage, will be able to quickly and efficiently move the valve member away from its second, or energized, position once the solenoid assembly is de-energized. The air- assist passage provides the necessary mechanical impetus to assist in moving the valve member to the de-energized position. [0008] Thus, the directly operated valve assembly of the present invention overcomes the shortcoming and drawbacks of conventional valve assemblies when they are so reduced in size such that the biasing member alone is of insufficient physical size and mechanical strength to repeatedly, quickly, and efficiently overcome the inertia of the valve member and/or exceed the fiictional adhesion forces acting at the valve bore. This allows a very fast acting valve assembly to be constructed in sizes below the conventional standards. BRIEF DESCRIPTION OF THE DRAWINGS [0009] Other advantages of the invention will be readily appreciated as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings, wherein: [0010] Figure 1 is a perspective view of a directly operated valve assembly having an air assist return of the present invention; [0011] Figure 2 is a cross-sectional side view of a directly operated valve assembly shown in Figure 1 illustrating the position of the valve member when the solenoid is de-energized; [0012] Figure 3 is a partial cross-sectional side view of a directly operated valve assembly illustrating the position of the valve member when the solenoid is energized; [0013] Figure 4 is a partial cross-sectional side view of another embodiment of a directly operated valve assembly of the present invention illustrating the position of the valve member when the solenoid is de-energized; [0014] Figure 5 is a partial cross-sectional side view of the directly operated valve assembly shown in Figure 4 illustrating the position of the valve member when the solenoid is energized. [0015] Figure 6 is a partial cross-sectional side view of still another embodiment of a directly operated valve assembly of the present invention illustrating the position of the valve member when the solenoid is de-energized. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT(S) [0016] Referring now to the figures where like numerals are used to designate like structure throughout the drawings, one embodiment of a directly operated valve assembly of the present invention is generally indicated at 10 in Figures 1-3. The valve assembly 10 includes a valve body 12 and an electromagnetic actuator, generally indicated at 14, mounted to the valve body 12. The valve body 12 has a thin rectangular shape defining top and bottom surfaces 16, 18, respectively, a pair of opposed side surfaces 20, 22 extending between the top and bottom surfaces 16 and 18 and end surfaces 24, 26. The actuator, shown as solenoid assembly 14, is mounted to the end surface 24 of the valve body 12. [0017] Referring now to Figures 2 and 3, the valve body 12 includes a pressurized fluid inlet port 30 for communicating with a source of pressurized fluid, such as air. Furthermore, the valve body 12 includes at least one cylinder port 32. A valve bore 36 extends axially through the valve body 12. In the embodiment illustrated in Figures 1 - 3, the directly operated valve assembly 10 is a three-way valve and includes at least one cylinder port 32, and at least one exhaust port 38 each in fluid communication with the valve bore 36. In this embodiment, the cylinder port 32 is formed through the top surface 16 of the valve body 12 opposite the inlet port 30 and the exhaust port 38 is formed through the bottom surface 18. However, those having ordinary skill in the art will appreciate that the various ports may be formed through various, different, surfaces of the valve body 12. For example, these ports and passages may all be formed through one surface, such as the bottom 18 of the valve body 12, without departing from the scope of the invention. The inlet port 30, exhaust and cylinder ports 38 and 32, respectively may also be threaded to accommodate any mechanism necessary to establish fluid communication with another component that is operatively associated with the valve assembly 10. To this end, the valve body 12 is adapted to be mounted to a manifold, sub-base, or any of a number of various pneumatically actuated devices (not shown). [0018] As shown in Figures 2-3, the valve bore 36 extends completely through the valve body 12 to present a pair of open ends 42, 44. A valve member, generally indicated at 46, is movable between predetermined positions within the valve bore 36 to selectively direct pressurized air from the inlet port 30 through the cylinder port 32 and the exhaust port 38 as will be described in greater detail below. A pair of end retainers 48 and 50 are received in the pair of open ends 42, 44, respectively, of the valve body 12 and act to retain the valve member 46 within the valve bore 36 as will be described in greater detail below. [0019] The valve member 46 further includes a pair of opposed valve heads 60 and 62 disposed at either end of the valve member 46 and at least one valve element 54, 56 that is formed on the valve member 46 between the opposed valve heads 60, 62. The valve element 54, 56 is operable to selectively direct a flow of pressurized air from the inlet port 30 through the valve bore 36 to either the cylinder port 32 or exhaust port 38. Each of the end retainers 48, 50 has a central bore 74, 76, respectively, that receives opposite heads 60, 62 of the valve member 46 and allows the valve member to slidingly move within the valve body 12. As best shown in Figure 3, the valve member 46 includes annular grooves 70 that receive o-ring type seals 72 that slidingly engage the central bore openings 74, 76, respectively, defined in the end retainers 48, 50 to prevent leakage of pressurized air within the valve bore 36. In one embodiment, the valve member 46 may be a poppet valve that is supported within the valve bore 36 for reciprocal movement therein to control the flow of fluid through the valve body 12. In this case, the poppet valve member 46 is preferably an aluminum insert over molded and bonded with rubber in specific areas of the valve member 46 and ground to specific dimensions to form, for example, the valve elements 54, 56. However, from the description that follows, those having ordinary skill in the art will appreciate that the present invention is not limited in any way to use in connection with a poppet valve. Rather, the present invention may be employed in connection with any other directly operated valve including, but not limited to, for example, spool valves, flat rubber poppet valves, flapper valves, pilot valves, or valve assemblies employed adjacent to or remote from the pneumatically actuated device. [0020] The end retainer 50 is cup-shaped and includes a plurality of cylinder passages 64 defined in the end retainer 50 and spaced radially relative to one another. The cylinder passages 64 provide fluid communication between the valve bore 36 and the respective adjacent ports. A biasing member 66 is positioned between the end retainer 50 and a recess 68 formed in one of the opposed valve heads 62 of the valve member 46. In the preferred embodiment, the biasing member is a coiled spring 66. However, those having ordinary skill in the art will appreciate that any biasing mechanism commonly known in the art that is sufficient to provide a force in one direction may be suitable for use in this application. Furthermore, those having ordinary skill in the art will appreciate that, because of the sheer number of suitable biasing members that may be employed in this environment, it is not efficient to attempt to catalog all of them here. Rather, it should be sufficient for purposes of description and illustration to mention that the return spring 66 applies a constant biasing force against the valve member 46 and to the left as viewed in Figures 2 and 3. Furthermore, the same is true with respect to the other embodiments described with respect to Figures 4-6 of the present application. [0021] A plurality of valve seats 84, 86 are presented in the valve bore 36. The valve seats 84 and 86 cooperate with the valve elements 54, 56 to seal the various passages in the valve body 12 as will be described in greater detail below. The valve seats 84, 86 provide sealing contact with the valve sealing surfaces of the valve elements 54, 56 when the valve member 46 is in a closed position relative to a particular port thereby interrupting the flow of pressurized air in that port. [0022] At least one of the valve seats, and in this case valve seat 84, may be formed directly on the valve bore 36 itself. The other valve seat 86 may be defined near the terminal end 51 of the end retainer 48 or 50. In the embodiment illustrated in Figures 2 and 3, the valve seat 86 is disposed upon the terminal end 51 of the retainer 50. The end retainer 50 is threadably adjustable within the valve bore 36 of the valve body 12 and therefore may be adjustably positioned within the end 44 of the valve bore 36. Thus, the threadably set position of the end retainer 50 within the valve body 12 controls the sealing of the valve seats 84, 86 with a given force applied to the valve member 46. The position to which the terminal end 51 of the end retainer 50 is located within the valve bore 36 defines the predetermined "open" and "closed" positions of the valve assembly 10 and thereby sets the stroke length of the valve member 46. To prevent leakage of the pressurized air within the valve bore 36, the end retainer 50 further includes annular grooves 91 and 93 that receive o-ring type seals 92, and the valve body 12, at the end retainer 48, further includes an annular groove 80 that receives an o-ring type seal 82. [0023] As noted above and illustrated in Figures 1-3, the electromagnetic actuator 14 is a solenoid assembly mounted to the end surface 24 of the valve body 12. The poppet valve member 46 is actuated in one direction, or to the right as viewed in Figure 2, under the influence of the solenoid assembly 14. To this end, the solenoid assembly 14 includes a housing, generally indicated at 100. The housing 100 includes a pole plate 102 abutting the valve body 12, a cap 104 disposed opposite the pole plate 102 and a solenoid can or frame 106 extending therebetween. The frame 106 supports a coil 108 including a conductive wire, schematically indicated at 110, conventionally wrapped around a bobbin 112. The conductive wire 110 is connected to a source of electrical current through leads, generally indicated at 114. The leads 114 are supported in the cap 104 and include lead pins 116, electrical contacts 118 and lead wires 120. The lead wires 120 are operatively connected to a source of electrical current. The direction of the current through the coil 108 and thus the direction of the electromagnetic force generated thereby is controlled by a control circuit (not shown). A top plate 122 is mounted adjacent to the bobbin 112 and between a portion of the frame 106 and the cap 104. [0024] The pole plate 102 includes an opening 124 extending therethrough. The solenoid assembly 14 further includes a ferromagnetic pole piece 126 having a stepped portion 128 with a smaller cross-sectional area than the rest of the pole piece 126. The stepped portion 128 is received in the opening 124 of the pole plate 102 for mechanically fixing the pole piece 126 to the pole plate 102. A centrally located passage 131 extends through the pole piece 126. A pushpin 132 is movably supported in the passage 131. [0025] A ferromagnetic armature 138 is disposed between the cap 104 and the pole piece 126. A bushing 140 guides the armature 138 within the bobbin 112. The armature 138 is movable toward the pole piece 126 under the influence of an electromagnetic flux generated by a pulse of current flowing through the coil 108 in one direction. This flux drives the armature 138 against the pushpin 132 to move the valve member 46 to the right as viewed in Figures 2-3 and to one predetermined position. Furthermore, the armature 138 is movable away from the pole piece 126 and toward the cap 104 (to the left as viewed in the Figures) under the influence of a force generated in the opposite direction as will be described in greater detail below. [0026] To this end, the pushpin 132 presents an enlarged head 142 which is disposed adjacent one end of the poppet valve member 46 for contacting it when the armature 138 contacts the pushpin 132. [0027] While a particular electromagnetically actuated device has been described above, the actuator employed with the valve assembly of the present invention may be of any known type used in pneumatic valves such as a self-latching electromagnetic solenoid of the type described in U.S. Patent No. 6,129,115 issued on October 10, 2000. Alternatively, the actuator may be an electromagnetic solenoid having a floating armature with lost-motion biasing such as described in prior art U.S. Patent Nos. 4,438,418 or 3,538,954. Each of these patents are assigned to the assignee of the present invention and the disclosures of these patents are incorporated herein by reference. Thus, those having ordinary skill in the art will appreciate from the description that follows that the exact form of the actuator, whether electromagnetic or otherwise, forms no part of the present invention. It should be further appreciated from the description of the invention that follows that, although the preferred embodiment of the pneumatic valve assembly 10 of the present invention is depicted as a three-way valve in Figures 1-3, the present invention may also be alternately embodied in the form of a two-way valve (not shown), a four-way valve (as shown in Figure 4-5), or the like. [0028] When the valve member 46 has been moved by the solenoid assembly 14 to the right as illustrated in Figure 3, the valve element 56 is moved into sealing engagement with the valve seat 86 defined on the terminal end 51 of the end retainer 50. In this operative disposition, fluid communication between the inlet port 30 and the cylinder port 32 is established and pneumatic pressure may be delivered to any down stream device. However, when the valve member 46 is in this operative disposition, frictional and adhesive forces may be generated at the interface between the valve member 46 and the central bore openings 74, 76 of the end retainers 48, 50. These forces act to resist the biasing force generated in the opposite direction by the biasing member 66 once the solenoid assembly 14 has been de-energized. Thus, these forces act to degrade the speed and efficiency at which the valve member 46 is returned to its first position. In addition, a reduction in the size of the biasing member 66 may result in a reduction of the force generated thereby resulting in a slower valve response time. [0029] In order to overcome this problem, the valve assembly 10 of the present invention includes an air-assist passage, generally indicated at 94. In the embodiment illustrated in Figures 1-3, the air assist passage 94 is formed within the valve member 46 and provides fluid communication between at least one cylinder port 32 and the recess 68 in the valve head 62 of the valve member 46. Thus, the air assist passage 94 provides selective fluid communication between the source of pressurized air and the recess 68. More specifically, and as illustrated in Figures 2 and 3, the air assist passage 94 includes an inlet portion 96 and a main passage 98. The inlet portion 96 extends radially relative to the centerline "A" of the valve member. In this representative embodiment, the inlet portion 96 is formed between valve elements 54, 56 and between the valve seats 84, 86 defined in the valve bore 36. The main passage 98 provides fluid communication between the inlet portion 96 and the recess 68. In this representative embodiment, the main passage 98 is coaxial relative to the longitudinal axis A of the valve member. [0030] The air-assist passage 94 provides a source of pneumatic pressure from the pressurized cylinder port 32 that acts in combination with the biasing member 66 to operatively move the valve member 46 in a direction opposite to the movement induced by the actuator 14. Importantly, the air assist facilitates a faster acting valve. More specifically, a valve assembly 10 employing the air assist of the present invention may include a smaller biasing member 66 that generates less force than would be required without the air assist. Because the biasing member 66 generates less force, the actuator 14 has less force to overcome and therefore moves the valve member 46 to its first position faster. In addition, the biasing member 66, along with the air assist provided through the passage 94, will be able to quickly and efficiently move the valve member 46 away from its second, or energized, position once the solenoid assembly 14 is de-energized. The air-assist passage 94 provides the necessary mechanical impetus to assist in moving the valve member 46 to the de-energized position. [0031J Thus, the directly operated valve assembly of the present invention overcomes the shortcoming and drawbacks of conventional valve assemblies when they are so reduced in size such that the biasing member 66 alone is of insufficient physical size and mechanical strength to repeatedly, quickly, and efficiently overcome the inertia of the valve member 46 and/or exceed the frictional adhesion forces acting at the interface between the valve member 46 and the central bore openings 74 and 76 of the end retainer 48, 50. This allows a very fast acting valve assembly 10 to be constructed in sizes below the conventional standards. [0032] Referring now to Figures 4-5, an alternate, non-limiting embodiment of a directly operated valve assembly having an air assist return of the present invention is generally indicated at 210, where like numerals increased by 200 with respect to the embodiment illustrated in Figures 1-3 are used to designate like structure . The valve assembly 210 illustrated in Figures 4 and 5 includes a valve body 212 having a pressurized fluid inlet port 230 for communicating with a source of pressurized fluid, such as air. Furthermore, the valve body 212 includes at least one cylinder passage, or outlet port 232, that is adapted for fluid communication with one or more pneumatically actuated devices. A valve bore 236 extends axially through the valve body 212. In the embodiment illustrated here, the pneumatic valve assembly 210 is a four-way valve and includes a pair of outlet ports 232, 234 and a pair of exhaust ports 238, 240 each in fluid communication with the valve bore 236. The outlet ports 232, 234 are formed through the top surface 216 of the valve body 212 opposite the inlet port 230 and exhaust ports 238, 240, which are formed through the bottom surface 218. However, those having ordinary skill in the art will appreciate that the inlet port 230, outlet and exhaust ports 232, 234 and 238, 240, respectively, may be formed through the various surfaces of the valve body 212. For example, these ports may all be formed through one surface, such as the bottom 218 of the valve body 212, without departing from the scope of the invention. The inlet port 230, outlet and exhaust ports 232, 234 and 238, 240, respectively may also be threaded to accommodate any mechanism necessary to establish fluid communication with another element that is operatively associated with the valve assembly 210. [0033] In the preferred embodiment illustrated in Figures 4-5, the valve bore 236 may extend completely through the valve body 212 to present a pair of open ends 242, 244. A valve member, generally indicated at 246, is movably supported within the valve bore 236 between predetermined positions to selectively direct a flow of pressurized air from the inlet port 230 through the valve bore 236 to at least one of the outlet ports 232, 234. Concomitantly, the valve member 246 may also selectively direct pressurized air to vent from at least one of the outlet ports 232, 234 to at least one of the exhaust ports 238, 240, as will be described in greater detail below. A pair of end retainer inserts, generally indicated at 248 and 250, are received in the pair of open ends 242, 244 of the valve body 212, thereby retaining the valve member 246 within the valve bore 236 as will be described in greater detail below. Similarly, the valve assembly 210 may include one or more inner retainers that are threadably positioned within the valve bore 236. In the embodiment illustrated herein, the valve assembly 210 includes one inner retainer 251 that is threadably positionable within the valve bore 236 as will be described in greater detail below. [0034] The valve member 246 further includes a pair of opposed valve heads 260, 262 disposed at either end of the valve member 246 and at least one valve element formed on the valve member 246 between the valve heads 260, 262. In the specific embodiment illustrated in Figures 4 and 5, a plurality of valve elements 252, 254, 256, and 258 are formed on the valve member 246 and are each operable to selectively direct a flow of pressurized air from an inlet port 230 through the valve bore 236 to the respective outlet ports 238, 240. As shown in Figures 4 and 5, the valve member 246 further includes annular grooves 270 that receive o-ring type seals 272, which slidingly engage the central bore openings 274, 276 respectively, of the retainer inserts 248, 250 to prevent leakage of the pressurized air within the valve bore 236. In the preferred embodiment, the valve member 246 is an aluminum insert that is over-molded with a suitable resilient material such as rubber, or any known elastomer, in the appropriate places. More specifically, it should be appreciated by those having ordinary skill in the art that the material of the sealing surface may be made of any known composition that is slightly yielding, yet highly resilient, such as nitrile, which may be bonded, or over-molded to the valve element 246. However, from the description that follows, those having ordinary skill in the art will appreciate that the present invention is not limited in any way to use in connection with the specific valve illustrated in Figures 4-5. Rather, the present invention may be employed in connection with any other directly operated valve including, but not limited to, for example, spool valves, flat rubber poppet valves, flapper valves, pilot valves, or valve assemblies employed adjacent to or remote from the pneumatically actuated device. [0035] The end retainer inserts 248 and 250 each include a plurality of cylinder passages 264 defined in the diameter of the retainers that spaced radially relative to one another. The cylinder passages 264 provide fluid communication between the valve bore 236 and the respective adjacent ports. A biasing member 266, such as a coiled spring, is positioned between the cup- shaped end retainer insert 250 and a recess 268 formed in one of the opposed valve heads 262 of the valve member 246. The return spring 266 applies a constant biasing force against the valve member 246 and to the left as viewed in Figures 4 and 5. [0036] A plurality of valve seats 282, 284, 286, and 288 are presented in the valve bore 236. The valve seats 282, 284, 286, and 288 cooperate with the valve elements 252, 254, 256, and 258, respectively, to seal the various passages in the valve body 212 as will be discussed in greater detail below. The valve seats 282, 284, 286, and 288 provide a sealing contact with the valve sealing surfaces of the valve elements 252, 254, 256, and 258 when the valve member 246 is in a closed position, relative to a particular outlet port, thereby interrupting the flow of pressurized air to that port. [0037] Of the plurality of valve seats 282, 284, 286, and 288 shown in Figures 4 and 5, some may be formed directly in the valve bore 236 itself, as in the case of valve seat 284, while others (e.g., valve seats 282, 286, and 288) may be disposed upon the end retainer inserts 248, 250 and inner retainer 251. The retainer inserts 248, 250, and 251 may be adjustably positioned within the valve bore 236 of the valve body 212, having a threadable interaction with the ends 242, 244 or any other suitable portion of the valve bore 236. As discussed above, each of the retainer inserts 248, 250 has a central bore 274, 276 that receives the opposed heads 260, 262 of the valve member 246 and allows it to slidingly move within the valve body 212. Thus, the threadably set position of the end retainer inserts 248, 250 within the valve body 212 controls the sealing of the valve seats with a given force applied to the valve member 246. The end retainer inserts 248, 250 further include annular grooves 291 and 293 which receive o-ring type seals 295 to prevent leakage of the pressurized air within the valve bore 236. On the other hand, the positions to which the inner retainer insert 251 is threadably set defines the predetermined "open" and "closed" positions of the valve assembly 210 and thereby sets the stroke length of the valve member 246. And like the end retainer inserts, the inner retainer 251 may also include an annular groove 297 which is adapted to receive an o-ring type seal 299 so as to prevent leakage of the pressurized air within the valve bore 236. [0038] In the preferred embodiment, the central bore 274 of retainer insert 248, which receives the end 260 of the valve member 246 also extends fully through the retainer allowing the actuator assembly 214 to engage and thereby actuate the valve member 246. As shown for illustration purposes only, this may be accomplished by the use of an actuator pushpin 332 having an enlarged head 342 that extends into the retainer insert 248 to engage and actuate the valve member 246. As alluded to above, it should be appreciated by those of ordinary skill in the art that the specific actuating means used to provide motive force to the valve member 246 lies beyond the scope of the present invention. Accordingly, it should be further appreciated that any number of different types of actuating elements, rather than a push pin, may be employed based on the actuating means used. The actuator assembly 214, as previously mentioned, is used to selectively actuate the valve member 246 within the valve bore 236 in the direction opposite to the biasing force of the biasing member 266. In this manner, the actuator assembly 214 drives the valve member to the right, as shown in Figure 4, and the biasing member 266 returns the valve member 246 to its original position (to the left, in Figure 5) when the actuator assembly 214 is deactivated. [0039] When the valve member 246 has been moved by the solenoid assembly 214 to the right as illustrated in Figure 4, the valve element 256 is moved into sealing engagement with the valve seat 286 defined on the inner retainer 251. In this operative disposition, fluid communication between the inlet port 230 and the cylinder port 232 is established and pneumatic pressure may be delivered to any down stream device. However, when the valve member 246 is in this operative disposition, rrictional and adhesive forces may be generated at the interface between the valve element 256 and valve seat 286. These forces act to resist the biasing force generated in the opposite direction by the biasing member 266 once the solenoid assembly 214 has been de-energized. Thus, these forces act to degrade the speed and efficiency at which the valve member 246 is returned to its first position. [0040] In order to overcome this problem, an air-assist passage, generally indicated at 294, is formed within the valve member 246 and extends between at least one cylinder port 232 and the recess 268 in the valve head 262 of the valve member 246 to provide selective fluid communication between the source of pressurized air and the recess 294. More specifically, and as illustrated in Figures 4 and 5, the air assist passage 294 includes an inlet portion 296 and a main passage 298. The inlet portion 296 extends radially relative to the centerline A of the valve member. In this representative embodiment, the inlet portion 296 is formed between a pair of valve elements 252, 254. The main passage 298 provides fluid communication between the inlet portion 296 and the recess 268 formed in the head 262 of the valve member 246. In this representative embodiment, the main passage 298 is coaxial relative to the longitudinal axis A of the valve member 246. [0041] The air-assist passage 294 provides a source of pneumatic pressure from the pressurized cylinder port 232 that acts in combination with the biasing member 266 to operatively move the valve member 246 in a direction opposite to the movement induced by the actuator 214. Importantly, the air assist facilitates a faster acting valve. More specifically, the valve assembly 210 employing the air assist of the present invention may include a smaller biasing member 266 that generates less force than would be required without the air assist. Because the biasing member 266 generates less force, the actuator 214 has less force to overcome and therefore moves the valve member 246 to its first position faster. In addition, the biasing member 266, along with the air assist provided through the passage 294, will be able to quickly and efficiently move the valve member 246 away from its second, or energized, position once the solenoid assembly 214 is de-energized. The air-assist passage 294 provides the necessary mechanical impetus to assist in moving the valve member 246 to the de-energized position. [0042] Thus, the directly operated valve assembly of the present invention overcomes the shortcoming and drawbacks of conventional valve assemblies when they are so reduced in size such that the biasing member 266 alone is of insufficient physical size and mechanical strength to repeatedly, quickly, and efficiently overcome the inertia of the valve member 246 and/or exceed the factional adhesion forces acting at the interface of the valve member 246 and the central bore openings 274 and 276 of the end retainer inserts 248, 250. This allows a very fast acting valve assembly 210 to be constructed in sizes below the conventional standards. [0043] Referring now to Figures 6, another, alternate non-limiting embodiment of a directly operated valve assembly having an air assist return of the present invention is generally indicated at 310, where like numerals increased by 300 with respect to the embodiment illustrated in Figures 1-3 are used to designate like parts. More specifically, the valve assembly 310 illustrated here is also a three-way valve and includes many of the same or similar components of the type described in connection with the three- and four-way valves illustrated in Figures 1-5. Accordingly, those having ordinary skill in the art will appreciate that the following description is presented in such a way so as to highlight the salient features of the present invention and does not include a restatement of the discussion of all like components of the valve assembly of the type described above. [0044] With this in mind, the valve assembly 310 includes a valve body 312 having a pressurized fluid inlet port 330 for communicating with a source of pressurized fluid, such as air. A valve bore 336 extends axially within the valve body 312. The valve body 312 also includes a cylinder port 332 and an exhaust port 338 both in fluid communication with the valve bore 336. A valve member 346 is moveably supported within the valve bore 336 and has a pair of opposed heads 360, 362. In addition, the valve member 346 includes at least one valve element 354, 356 that is operable to selectively direct a flow of pressurized air from the inlet port 330 through the valve bore 336 to either the cylinder port 332 or the exhaust port 338. A plurality of valve seats 384, 386 are presented in the valve bore 336. The valve seats 384 and 386 cooperate with the valve element 354, 356 to seal the various passages in the valve body 312 as will be described in greater detail below. The valve seats 384, 386 provide sealing contact with the valve sealing surfaces of the valve elements 354, 356 when the valve member 346 is in a closed position relative to a particular port thereby interrupting the flow of pressurized air in that port. [0045] Unlike the open ended valve bores illustrated in Figures 1-5, the valve bore 336 is a blind bore having an open end 342 and a closed end 344. An electromagnetic actuator, such as a solenoid assembly, generally indicated at 314, is mounted to the valve body 312 at the open end 342 of the valve bore 336. The solenoid assembly 14 acts to bias the valve member 346 in one direction in the same manner as described with respect to the embodiments illustrated in Figures 1-5. On the other hand, a biasing member 366, such as a coiled spring, is positioned between the blind end 344 of the valve bore 336 and a recess 368 formed in one of the opposed valve heads 362 of the valve member 346. The return spring 366 applies a constant biasing force against the valve member 346 in a direction opposite to the force applied by the solenoid assembly 314. [0046] When the valve member 346 has been moved by the solenoid assembly 314 downwardly, relative to Figure 6, the valve element 356 is moved into sealing engagement with the valve seat 386 defined in the valve bore 336. In this operative disposition, fluid communication between the inlet port 330 and the cylinder port 332 is established and pneumatic pressure may be delivered to any downstream device. However, when the valve member 346 is in this operative disposition, frictional and adhesive forces may be generated at the interface between the seals 372 on the valve member 246 and the ends 342, 344 of the central bore 336. These forces act to resist the biasing force generated in the opposite direction by the biasing member 366 once the solenoid assembly 314 has been de-energized. As noted above, these forces act to degrade the speed and efficiency at which the valve member 346 is returned to its first position. [0047] In order to overcome this problem, an air assist passage, generally indicated at 394, is formed within the valve body 312 and provides fluid communication between the cylinder port 332 and the recess 368 in the valve head 362 of the valve member 346. Thus, the air assist passage 394 provides selective fluid communication between the source of pressurized air and the recess 368. However, those having ordinary skill in the art will note that the air assist passage 394 differs from the air assist passages 94 and 294 in that it is defined within the valve body 312 as opposed to the valve member 46, 246. More specifically, and as illustrated in Figure 6, the air assist passage 394 includes an inlet portion 396 and a main passage 398. The inlet portion 396 extends axially within the valve body 312 relative to the movement of the valve member 346 and provides fluid communication between the cylinder port 332 and the main passage 398. On the other hand, and in this representative embodiment, the main passage 398 extends transverse to the longitudinal axis A of the valve member 346 and provides fluid communication between the inlet portion 396 and the recess 368 formed in the valve head 362 of the valve member 346. [0048] The air-assist passage 394 provides a source of pneumatic pressure from the pressurized cylinder port 332 that acts in combination with the biasing member 366 to operatively move the valve member 346 in a direction opposite to the movement induced by the actuator 314. Importantly, the air assist facilitates a faster acting valve. More specifically, a valve assembly 310 employing the air assist of the present invention may include a smaller biasing member 366 that generates less force than would be required without the air assist. Because the biasing member 366 generates less force, the actuator 314 has less force to overcome and therefore moves the valve member 346 to its first position faster. In this way, the biasing member 366, along with the air assist provided through the passage 394, will be able to quickly and efficiently move the valve member 346 away from its energized, position once the solenoid assembly 314 is de-energized. The air-assist passage 394 provides the necessary mechanical impetus to assist in moving the valve member 346 to the de-energized position. Thus, the directly operated valve assembly of the present invention overcomes the shortcoming and drawbacks of conventional valve assemblies when they are so reduced in size such that the biasing member 366 alone is of insufficient physical size and mechanical strength to repeatedly, quickly, and efficiently overcome the inertia of the valve member 346 and/or exceed the frictional adhesion forces acting between the valve member 346 and the valve bore 336. This allows a very fast acting valve assembly 310 to be constructed in sizes below the conventional standards. OPERATION [0049] The operation of the directly operated pneumatic valve having an air assist return of the present invention will now be described with reference to the three-way valve assembly 10 illustrated in Figures 1-3. However, those having ordinary skill in the art will appreciate that the explanation of the operation of the valve illustrated in Figures 1-3 also applies with respect to the four-way valve illustrated in Figures 4 and 5 as well as the three-way valve illustrated in Figure 6 and any other directly operated pneumatic valve that employs the air assist return of the present invention. [0050] In operation, pressurized air is supplied to the inlet port 30. The pressurized air flows past a filter 31 disposed in that port and into the valve bore 36. When the solenoid assembly 14 is de-energized, the biasing member 66 biases the valve member 46 to the left as viewed in Figure 2 such that the valve element 54 is in sealing engagement with the valve seat 84. In this disposition, the valve element 56 is disposed spaced from the valve element 86 providing a flow passage between the cylinder port 32 and the valve bore 36. In this way, the cylinder port 32 is vented through the main valve bore 36 and the cylinder passages 64 and into the exhaust port 38. [0051] On the other hand, when the solenoid assembly 14 is energized, it produces a force that drives the valve member 46 to the right as viewed in Figure 3 and against the biasing force of the biasing member 66. In this operative disposition, the valve element 54 is moved off of the valve seat 84 and the valve element 56 is quickly moved into sealing engagement with the valve seat 86. Pressurized air is then allowed to flow through the inlet port 30, past the filter 31, into the valve bore 36, past the open valve element 54 and valve seat 84, and into the cylinder port 32. On the other hand, the interaction of the valve element 56 and valve element 86 seals the cylinder port 32 with respect to the exhaust port 38. In addition, the air assist passage 94 is open to the pressurized air flowing through the valve bore 36 and cylinder port 32. Thus, the recess 68 formed in the valve head 62 is similarly pressurized. However, the force generated by the solenoid assembly 14 is sufficient to overcome the oppositely directed force generated by this pressure. [0052] Once the solenoid assembly 14 is de-energized and the actuating force is removed from the valve head 60 of the valve member 46, the biasing member 66 and the air pressure acting on the valve head 62 cooperatively start to move the valve member 46 back to its first position. As this occurs, the valve element 56 that formed a seal in the energized position with the valve seat 86 will quickly move off valve seat 86, so that the cylinder port 32 that was pressurized (and providing the air-assist pressure) vents through the exhaust port 38. The valve member 46 is then moved to the left until the valve element 54 seals with the valve seat 84 and fluid communication between the cylinder port 32 and the exhaust port 38 is established past the valve element 56 and the valve seat 86 through the valve bore 36. It should be noted that, once the valve member 46 is moving and any frictional or adhesion forces acting at the valve element 56 are overcome, the biasing member 66 has enough mechanical strength to continue to move the valve member 46 to its first de-energized position and the air-assist is no longer needed. [0053] The air-assist passage provides a source of pneumatic pressure from the pressurized cylinder port that acts in combination with the biasing member to operatively move the valve member in a direction opposite to the movement induced by the actuator. Importantly, the air assist facilitates a faster acting valve. More specifically, valve assemblies employing the air assist of the present invention may include a smaller biasing member that generates less force than would be required without the air assist. Because the biasing member generates less force, the actuator has less force to overcome and therefore moves the valve member to its first position faster. The biasing member, along with the air assist provided through the passage, will be able to quickly and efficiently move the valve member away from its second, or energized, position once the solenoid assembly is de-energized. The air-assist passage provides the necessary mechanical impetus to assist in moving the valve member to the de-energized position. Thus, the directly operated valve assembly of the present invention overcomes the shortcoming and drawbacks of conventional valve assemblies when they are so reduced in size such that the biasing member alone is of insufficient physical size and mechanical strength to repeatedly, quickly, and efficiently overcome the inertia of the valve member and/or exceed the frictional adhesion forces acting between the valve member and the central bore. [0054] The structure of the direct operated valve assembly 10, 210, and 310 of the present invention as described above has distinct advantages over the valves known in the related art. The valve assemblies 10, 210, and 310 are very fast acting. Further, the size limitations of convention valve assemblies are overcome and a range of smaller size valves become available. More specifically, the air-assist passage allows for a very fast acting valve assembly in a size much smaller than conventional designs. Thus, it is easily employed in environments where space is at a premium. The small size of the pneumatic valve of the present invention is facilitated by the air-assist passage providing a supplemental force of pressurized air to the biasing member. Furthermore, and from the foregoing description, those having ordinary skill in the art will readily appreciate that the air assist passage may be formed anywhere, either within the valve body, the valve member, partially exterior of the valve body, or any combination of these to provide a source of pneumatic pressure that acts in combination with the biasing member to operatively move the valve member in the direction opposite to the movement induced by the actuator. [0055] Once again, from the foregoing description, those having ordinary skill in the art will appreciate that the present invention is not limited in any way to use in connection with a poppet valve. Rather, the present invention may be employed in connection with any other directly operated valve including, but not limited to, for example, spool valves, flat rubber poppet valves, flapper valves, pilot valves, or valve assemblies employed adjacent to or remote from the pneumatically actuated device. [0056] The invention has been described in an illustrative manner. It is to be understood that the terminology that has been used is intended to be in the nature of words of description rather than of limitation. Many modifications and variations of the invention are possible in light of the above teachings. Therefore, within the scope of the appended claims, the invention may be practiced other than as specifically described. WE CLAIM : ---------------- 1. A directly operated valve assembly comprising! a valve body having a pressurized air supply inlet port in communication with a source of pressurized air, and at least one cylinder port; a valve bore extending axially within said valve body; a valve member supported within said valve bore and positionable only between a first position and a predetermined second position within said valve bore to selectively direct pressurized air from said inlet port through said at least one cylinder port in said second positiont said valve member comprising a pair of opposed valve heads, at least one of said opposed valve heads having a recess; an actuator mounted to said valve body for moving said valve in a first direction to said second position and a biasing member disposed within said recess between said valve member and said valve body adapted to provide a biasing force to said valve member in an opposite second direction to move said valve member to said first position; and an air-assist passage providing a source of pneumatic pressure that acts in combination with said biasing member to operatively move said valve member in said second direction opposite to the movemement induced by said actuator, said air assist passage providing communication between said at least one cylider port and said source of pressurized air* said air-assist passage having s an inlet portion and a main passage, said inlet portion extending radially relative to the center line A of the valve member and providing fluid communication with said at least one cylinder port* and said main passage providing fluid communication between said inlet port and said recess; and wherein said inlet portion is formed between a pair of valve elements commonly over-molded with rubber on said valve member. 2. A directly operated valve assembly (10, 210, 310) as claimed in claim 1 wherein said valve member (46, 246, 346) comprises a pair of opposed valve heads (60, 62, 260, 262, 360, 362), at least one of said opposed valve heads having a recess (68, 268, 368), said biasing member (66, 266, 366) operatively disposed within said recess between said valve member (46, 246, 346) and said valve body (12, 212, 312). 3. A directly operated valve assembly (10, 210) as claimed in claim 2 wherein said air-assist passage (94, 294) is formed within said valve member (12, 212) and extends between said at least one cylinder port (32, 232) and said recess (68, 268) in said at least one opposed valve head (62, 262) of said valve member to provide selective fluid communication between said source of pressurized air and said recess (68, 268). 4. A directly operated valve assembly (10, 210) as claimed in claim 3 wherein said air assist passage (94, 294) comprises an inlet portion (96, 296) and a main passage (98, 298), said inlet portion (96, 296) extemding radially relative to the center line A of the valve member (46, 246) and providing fluid communication with said at least one cylinder port (32, 232), and said main passage (98, 298) providing fluid communication between said inlet port and said recess (68, 268). 5. A directly operated valve assembly (10, 210) as claimed in claim 4 wherein said main passage (98, 298) extends coaxially within said valve member (46, 246) relative to the longitudinal axis of the valve member. 6. A directly operated valve assembly (10) as claimed in claim 4 wherein said inlet portion (96) is formed between a pair of valve elements (54, 56) formed on said valve member (46). 7. A directly operated valve assembly (310) as claimed in claim 2 wherein said air assist passage (394) is formed within said valve body (312) and extends between said at least one cylinder port (332) and said recess (368) in said valve head (362) of said valve member (346) to provide selective fluid communication between said source of pressurized air and said recess (368). 8. A directly operated valve assembly (310) as claimed in claim 7 wherein said air assist passage (394) comprises an inlet portion (396) and a main passage (398), said inlet portion (396) extending axially within said valve body (312) relative to the movement of said valve member (346) within said valve bore (336) and provides fluid communication between said said at least one cylinder port (332) and said main passage (398)» said main passage (398) extending transversely relative to the longitudinal axis A of said valve member (346) and provides fluid communication between said inlet portion (396) and said recess (368) formed in said valve head (362) of said valve member (346). 9. A directly operated valve assembly (10, 210) as claimed in claim 1 wherein said valve bore (46, 246) extends through said valve body (12, 212) to present a pair of open ends (42, 44, 242, 244) and said assembly comprises a pair of retainer assemblies (48, 50, 248, 250) threadably received in said pair of open ends of valve body (12, 212) to close same. 10. A directly operated valve assembly (10, 210) as claimed in claim 9 wherein each of said pair of retainer assemblies (48, 50, 248, 250) defines an innermost terminal end, said valve member (46, 246) defining a poppet valve having a pair of opposed annular valve heads ( 60, 62, 260, 262) disposed at either end of said poppet valve, each of said pair of opposed valve heads defining an outer diameter moveably received in sealing engagement with said innermost terminal ends of said pair of retainer assemblies (48, SO, 248, 250). 11. A directly operated valve assembly (210) as claimed in claim 1 wherein said valve body (212) comprises a pair of cylinder ports (232, 234) and a pair of exhaust ports (238, 240) each in fluid communication with said valve bore (236), said valve bore having a plurality of valve seats (282, 284,286, 288), said valve member (246) comprises a plurality of valve elements (252, 254,256, 258) defined along its lenght, said valve elements cooperating with said valve seats to direct fluid from said valve bore (236) through various ones of said pair of cylinder ports (232, 234) and said pair of exhaust ports (23, 240). 12. A directly operated valve assembly (10, 210) comprising! a valve body (12, 212) having a pressurized air supply inlet port (30, 230) in communication with a source of pressurized air and at least one cylinder port (32, 232); a valve bore (36, 236) extending axially within said valve body (12, 212); a valve member (46, 246) having a pair opposed valve heads (60, 62, 260, 262) slidingly disposed within said valve bore (36, 236) and movable between predetermined first and second positions within said valve bore to selectively direct pressurized air from said inlet port (30, 230) through said at least one cylinder port (32, 232)? an actuator (14, 214) disposed upon said valve body (12, 212) at one end (60, 260) of said valve member for moving said valve member (46, 246) in one direction from said first to said second position; a biasing member (66, 266) disposed at the other end (62, 262) of said valve member between said valve member (46, 246) and said valve body (12, 212) adapted to providing a biasing force to said valve member; and an air-assist passage (94, 294) disposed within said valve member (46, 246) providing fluid communication between said biased end (623, 262) of said valve member and the source of pressurized air such that pneumatic pressure acts in combination with said biasing member (66, 266) to operatively move said valve member (46, 246) in a direction opposite to the movement produced by said actuator (14, 214) and from said second to said first position. 13. A directly operated valve assembly (10, 210) as claimed in claim 12 wherein at least one of said opposed valve heads (62, 262) comprises a recess (68, 268) said air assist passage (94, 294) comprises an inlet portion (96, 296) and a main passage (98, 298), said inlet portion (96, 296) extending radially relative to the center line A of said valve member (46, 246) and providing fluid communication with said at least one cylinder port (32, 232), and said main passage (98, 298) providing fluid commmunication between said inlet portion (96, 296) and said recess (68, 268). 14. A directly operated valve assembly (10, 210) as claimed in claim 13 wherein said main passage (96, 296) extends coaxially within said valve member (46, 246) relative to the longitudinal axis of the valve member. 15. A directly operated valve assembly (10) as claimed in claim 13 wherein said inlet portion is formed between a pair of valve elements (54, 56) formed on said valve member (46). 16. A directly operated valve assembly (310) comprising : a valve body (312) having a pressurized air supply inlet port (330) in communication with a source of pressurized air and at least one cylinder port (332); a valve bore (336) extending axially within said valve body (312)5 a valve member (346) having a pair of opposed valve heads (360, 362) slidingly disposed within said valve bore (336) and movable between predetermined first and second positions within said valve bore to selectively direct pressurized air from said inlet port (330) through said at least one cylinder port (332); an actuator (314) disposed upon said valve body (312) at one end of said valve member for moving said valve member (346) in one -direction from said first to said second position} a biasing member (366) disposed at the other end of said valve member between said valve member (346) and said valve body (312) adapted in providing a biasing force to said valve member; and an air assist passage (394) formed within said valve body (312) and extending between said at least one cylinder port (332) and one of said pair of opposed valve heads (362) to provide selective fluid communication between said source of pressurized air and said valve head (362). 17. A directly operated valve assembly (310) as claimed in claim 16 wherein said valve member(346)comprises a recess 268 formed in at least one valve head 362, said air assist passage (394) comprises an inlet portion (396) and a main passage (398)» said inlet portion (396) extending axially within said valve body (312) relative to the movement of said valve member within said valve bore and provides fluid communication between said at least one cylinder port (332) and said main passage (398), said main passage (398) extending traversely relative to the longitudinal axis of said valve member (346) and provides fluid communication between said inlet portion (330) and said recess (368) formed in said valve head (362) of said valve member (346). The invention relates to a directly operated valve assembly comprising a valve body having a pressurized air supply inlet port in communication with a source of pressurized air, and at least one cylinder port; a valve bore extending axially within said valve body; a valve member supported within said valve bore and positionable only betrween a first position and a predetermined second position within said valve bore to selectively direct pressurized air from said inlet port through said at least one cylinder port in said second position, said valve member comprising a pair of opposed valve heads, at least one of said opposed valve heads having a recess; an actuator mounted to said valve body for moving said valve member in a first direction to said second position and a biasing member disposed within said recess between said valve member and said valve body adapted to provide a biasing force to said valve member in an opposite second direction to move said valve member to said first position; and an air—assist passage providing a source of pneumatic pressure that acts in combination with said

Full Text

DIRECTLY OPERATED PNEUMATIC VALVE
HAVING AN AIR ASSIST RETURN
BACKGROUND OF THE INVENTION
1. Field of the Invention
[0001] The invention relates, generally, to pneumatic valve assemblies and, more
specifically, to a directly operated pneumatic valve having an air assist return.
2. Description of the Related Art
[0002] Directly operated, or actuated, pneumatic valves are well known in the art for
controlling the flow of pressurized air therethrough. Directly operated valves may be used alone
or in connection with, for example, spool valves and regulators that, in turn, control the flow of
pressurized air to and from various pneumatically actuated devices such as press clutches, air
brakes, air cylinders or any other pneumatic device or application requiring precise control of
operating air. More specifically, two-way, three-way and four-way direct operated valve
assemblies are commonly employed in these environments. Such valves typically include a valve
body having a valve bore formed in the valve body. A valve member is movably supported within
the valve bore from one position to another in direct response to an operative force placed on the
valve member by an actuator. A plurality of ports are used to connect the valve assembly to a
system supply pressure as well as the various active devices that the valve may control. The
actuator is typically an electromagnetically operated solenoid that is energized to move the valve
member to a predetermined position within the valve bore. A return spring is often employed to
bias the valve member back to a known non-energized position. Valves of this type are employed
in a wide variety of manufacturing environments where a high flow rate and very fast response
time are desired.
[0003] As the technology for these valves has advanced, there has been an increase in the
demand for smaller valves that are designed to be employed in operating environments with ever
decreasing physical dimensions. In addition, the advance in technology has dictated that the
valves must be able to operate with very fast cycle times. In fact, the demand for greater speed
and shorter response time is an ongoing requirement for valves of this type. However, in the past,
certain design barriers have limited the extent to which the size of the valve assembly could be
reduced while at the same time increasing its speed. When the valve member and the valve bore
are reduced below a predetermined size, the return spring may be of insufficient physical size and
mechanical strength to overcome the inertia of the valve member. In addition, after the valve
member has been biased in one direction by the actuator, frictional forces and surface adhesion
can build up at the interface of the valve member seals and the valve bore. These frictional forces
and related surface adhesion can act to inhibit movement of the valve member in the opposite
direction and reduce valve speed and therefore increase valve response time. In this case, the
return spring may be unable to provide enough biasing force to quickly or effectively move the
valve member from its energized position and return it to the non-energized position when the
actuator force is removed. When this occurs, accurate control of the active device is lost. To
counter this shortcoming, various design strategies have emerged. However, the design strategies
that have been proposed in the related art all suffer from the disadvantage that they add
supplemental mechanisms, hardware, or require a remote mounting of the valve.
[0004] For example, one design strategy proposed in the related art involves the use of
dual electromagnetic actuators to move the valve member in opposite directions. Thus, the return
spring is replaced by an electromagnetic actuator such as a solenoid. Unfortunately, this solution
adds the complexity of a second solenoid and its associated parts, and also creates another size
limiting boundary. On the other hand, single electromagnetic actuators that energize in both
directions have been suggested in the related art. However, these single electromagnetic actuators
require a bulkier double wound actuator as well as additional electronic circuitry and controls.
Thus, directly operated valves that employ the bulkier single electromagnetic operators are
typically mounted in a remote location relative to the pneumatically actuated device they control.
Unfortunately, the remotely located valves defeat the purpose of smaller, lighter, and more
accurate valve designs that can be mounted in very close proximity to the active devices. Also,
they must be interconnected via conduits or other flow passages, which require additional
hardware and plumbing, and can lower pneumatic efficiencies and introduce line losses within the
system.
[0005] While the use of the larger conventional valves, either remotely disposed or with
the addition of other components, has generally worked for their intended purposes, there remains
an ongoing need in the art to simplify pneumatic systems and thereby lower costs of manufacture
and/or assembly by creating ever smaller, yet highly accurate, fast actuating, directly operated
pneumatic valves. Smaller directly operated valves can be located in very close proximity to
active system components, thereby shortening flow paths, reducing or eliminating additional
plumbing and hardware, and increasing pneumatic flow efficiency. Unfortunately, the design
strategies that have been proposed in the related art have failed to overcome the problems created
when the valve member and bore are reduced in size past the point where a return spring has the
physical size and mechanical force to quickly, effectively, and repeatedly return the valve member
of a fast acting valve to the non-energized position.
SUMMARY OF THE INVENTION
[0006] The present invention overcomes these design barriers and other disadvantages of
the related art in a directly operated valve assembly. More specifically, the present invention is
directed toward a directly operated valve assembly including a valve body having a pressurized
air supply inlet port in communication with a source of pressurized air, and at least one cylinder
port. A valve bore extends axially within the valve body, and a valve member is moveably
supported within the valve bore between predetermined positions to selectively direct pressurized
air from the inlet port through the cylinder port. An actuator is mounted to the valve body for
moving the valve member in a first direction and a biasing member is disposed between the valve
member and the valve body to provide a biasing force to the valve member in an opposite
direction. Also, an air-assist passage is included for providing a source of pneumatic pressure that
acts in combination with the biasing member to operatively move the valve member in a direction
opposite to the movement induced by the actuator.
r00071 The directly operated valve assembly of the present invention has distinct
advantages over the valves known in the related art. The air-assist passage provides a source of
pneumatic pressure from the pressurized cylinder port that acts in combination with the biasing
member to operatively move the valve member in a direction opposite to the movement induced
by the actuator. Importantly, the air assist facilitates a faster acting valve. More specifically,
valve assemblies employing the air assist of the present invention may include a smaller biasing
member that generates less force than would be required without the air assist. Because the
biasing member generates less force, the actuator has less force to overcome and therefore moves
the valve member to its first position faster. In addition, the biasing member, along with the air
assist provided through the passage, will be able to quickly and efficiently move the valve member
away from its second, or energized, position once the solenoid assembly is de-energized. The air-
assist passage provides the necessary mechanical impetus to assist in moving the valve member
to the de-energized position.
[0008] Thus, the directly operated valve assembly of the present invention overcomes the
shortcoming and drawbacks of conventional valve assemblies when they are so reduced in size
such that the biasing member alone is of insufficient physical size and mechanical strength to
repeatedly, quickly, and efficiently overcome the inertia of the valve member and/or exceed the
fiictional adhesion forces acting at the valve bore. This allows a very fast acting valve assembly
to be constructed in sizes below the conventional standards.
BRIEF DESCRIPTION OF THE DRAWINGS
[0009] Other advantages of the invention will be readily appreciated as the same becomes
better understood by reference to the following detailed description when considered in
connection with the accompanying drawings, wherein:
[0010] Figure 1 is a perspective view of a directly operated valve assembly having an air
assist return of the present invention;
[0011] Figure 2 is a cross-sectional side view of a directly operated valve assembly shown
in Figure 1 illustrating the position of the valve member when the solenoid is de-energized;
[0012] Figure 3 is a partial cross-sectional side view of a directly operated valve assembly
illustrating the position of the valve member when the solenoid is energized;
[0013] Figure 4 is a partial cross-sectional side view of another embodiment of a directly
operated valve assembly of the present invention illustrating the position of the valve member
when the solenoid is de-energized;
[0014] Figure 5 is a partial cross-sectional side view of the directly operated valve
assembly shown in Figure 4 illustrating the position of the valve member when the solenoid is
energized.
[0015] Figure 6 is a partial cross-sectional side view of still another embodiment of a
directly operated valve assembly of the present invention illustrating the position of the valve
member when the solenoid is de-energized.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT(S)
[0016] Referring now to the figures where like numerals are used to designate like
structure throughout the drawings, one embodiment of a directly operated valve assembly of the
present invention is generally indicated at 10 in Figures 1-3. The valve assembly 10 includes a
valve body 12 and an electromagnetic actuator, generally indicated at 14, mounted to the valve
body 12. The valve body 12 has a thin rectangular shape defining top and bottom surfaces 16,
18, respectively, a pair of opposed side surfaces 20, 22 extending between the top and bottom
surfaces 16 and 18 and end surfaces 24, 26. The actuator, shown as solenoid assembly 14, is
mounted to the end surface 24 of the valve body 12.
[0017] Referring now to Figures 2 and 3, the valve body 12 includes a pressurized fluid
inlet port 30 for communicating with a source of pressurized fluid, such as air. Furthermore, the
valve body 12 includes at least one cylinder port 32. A valve bore 36 extends axially through the
valve body 12. In the embodiment illustrated in Figures 1 - 3, the directly operated valve
assembly 10 is a three-way valve and includes at least one cylinder port 32, and at least one
exhaust port 38 each in fluid communication with the valve bore 36. In this embodiment, the
cylinder port 32 is formed through the top surface 16 of the valve body 12 opposite the inlet port
30 and the exhaust port 38 is formed through the bottom surface 18. However, those having
ordinary skill in the art will appreciate that the various ports may be formed through various,
different, surfaces of the valve body 12. For example, these ports and passages may all be formed
through one surface, such as the bottom 18 of the valve body 12, without departing from the
scope of the invention. The inlet port 30, exhaust and cylinder ports 38 and 32, respectively may
also be threaded to accommodate any mechanism necessary to establish fluid communication with
another component that is operatively associated with the valve assembly 10. To this end, the
valve body 12 is adapted to be mounted to a manifold, sub-base, or any of a number of various
pneumatically actuated devices (not shown).
[0018] As shown in Figures 2-3, the valve bore 36 extends completely through the valve
body 12 to present a pair of open ends 42, 44. A valve member, generally indicated at 46, is
movable between predetermined positions within the valve bore 36 to selectively direct
pressurized air from the inlet port 30 through the cylinder port 32 and the exhaust port 38 as will
be described in greater detail below. A pair of end retainers 48 and 50 are received in the pair of
open ends 42, 44, respectively, of the valve body 12 and act to retain the valve member 46 within
the valve bore 36 as will be described in greater detail below.
[0019] The valve member 46 further includes a pair of opposed valve heads 60 and 62
disposed at either end of the valve member 46 and at least one valve element 54, 56 that is formed
on the valve member 46 between the opposed valve heads 60, 62. The valve element 54, 56 is
operable to selectively direct a flow of pressurized air from the inlet port 30 through the valve
bore 36 to either the cylinder port 32 or exhaust port 38. Each of the end retainers 48, 50 has a
central bore 74, 76, respectively, that receives opposite heads 60, 62 of the valve member 46 and
allows the valve member to slidingly move within the valve body 12. As best shown in Figure 3,
the valve member 46 includes annular grooves 70 that receive o-ring type seals 72 that slidingly
engage the central bore openings 74, 76, respectively, defined in the end retainers 48, 50 to
prevent leakage of pressurized air within the valve bore 36. In one embodiment, the valve
member 46 may be a poppet valve that is supported within the valve bore 36 for reciprocal
movement therein to control the flow of fluid through the valve body 12. In this case, the poppet
valve member 46 is preferably an aluminum insert over molded and bonded with rubber in specific
areas of the valve member 46 and ground to specific dimensions to form, for example, the valve
elements 54, 56. However, from the description that follows, those having ordinary skill in the
art will appreciate that the present invention is not limited in any way to use in connection with
a poppet valve. Rather, the present invention may be employed in connection with any other
directly operated valve including, but not limited to, for example, spool valves, flat rubber poppet
valves, flapper valves, pilot valves, or valve assemblies employed adjacent to or remote from the
pneumatically actuated device.
[0020] The end retainer 50 is cup-shaped and includes a plurality of cylinder passages 64
defined in the end retainer 50 and spaced radially relative to one another. The cylinder passages
64 provide fluid communication between the valve bore 36 and the respective adjacent ports. A
biasing member 66 is positioned between the end retainer 50 and a recess 68 formed in one of the
opposed valve heads 62 of the valve member 46. In the preferred embodiment, the biasing
member is a coiled spring 66. However, those having ordinary skill in the art will appreciate that
any biasing mechanism commonly known in the art that is sufficient to provide a force in one
direction may be suitable for use in this application. Furthermore, those having ordinary skill in
the art will appreciate that, because of the sheer number of suitable biasing members that may be
employed in this environment, it is not efficient to attempt to catalog all of them here. Rather, it
should be sufficient for purposes of description and illustration to mention that the return spring
66 applies a constant biasing force against the valve member 46 and to the left as viewed in
Figures 2 and 3. Furthermore, the same is true with respect to the other embodiments described
with respect to Figures 4-6 of the present application.
[0021] A plurality of valve seats 84, 86 are presented in the valve bore 36. The valve
seats 84 and 86 cooperate with the valve elements 54, 56 to seal the various passages in the valve
body 12 as will be described in greater detail below. The valve seats 84, 86 provide sealing
contact with the valve sealing surfaces of the valve elements 54, 56 when the valve member 46
is in a closed position relative to a particular port thereby interrupting the flow of pressurized air
in that port.
[0022] At least one of the valve seats, and in this case valve seat 84, may be formed
directly on the valve bore 36 itself. The other valve seat 86 may be defined near the terminal end
51 of the end retainer 48 or 50. In the embodiment illustrated in Figures 2 and 3, the valve seat
86 is disposed upon the terminal end 51 of the retainer 50. The end retainer 50 is threadably
adjustable within the valve bore 36 of the valve body 12 and therefore may be adjustably
positioned within the end 44 of the valve bore 36. Thus, the threadably set position of the end
retainer 50 within the valve body 12 controls the sealing of the valve seats 84, 86 with a given
force applied to the valve member 46. The position to which the terminal end 51 of the end
retainer 50 is located within the valve bore 36 defines the predetermined "open" and "closed"
positions of the valve assembly 10 and thereby sets the stroke length of the valve member 46. To
prevent leakage of the pressurized air within the valve bore 36, the end retainer 50 further includes
annular grooves 91 and 93 that receive o-ring type seals 92, and the valve body 12, at the end
retainer 48, further includes an annular groove 80 that receives an o-ring type seal 82.
[0023] As noted above and illustrated in Figures 1-3, the electromagnetic actuator 14 is
a solenoid assembly mounted to the end surface 24 of the valve body 12. The poppet valve
member 46 is actuated in one direction, or to the right as viewed in Figure 2, under the influence
of the solenoid assembly 14. To this end, the solenoid assembly 14 includes a housing, generally
indicated at 100. The housing 100 includes a pole plate 102 abutting the valve body 12, a cap 104
disposed opposite the pole plate 102 and a solenoid can or frame 106 extending therebetween.
The frame 106 supports a coil 108 including a conductive wire, schematically indicated at 110,
conventionally wrapped around a bobbin 112. The conductive wire 110 is connected to a source
of electrical current through leads, generally indicated at 114. The leads 114 are supported in the
cap 104 and include lead pins 116, electrical contacts 118 and lead wires 120. The lead wires 120
are operatively connected to a source of electrical current. The direction of the current through
the coil 108 and thus the direction of the electromagnetic force generated thereby is controlled
by a control circuit (not shown). A top plate 122 is mounted adjacent to the bobbin 112 and
between a portion of the frame 106 and the cap 104.
[0024] The pole plate 102 includes an opening 124 extending therethrough. The solenoid
assembly 14 further includes a ferromagnetic pole piece 126 having a stepped portion 128 with
a smaller cross-sectional area than the rest of the pole piece 126. The stepped portion 128 is
received in the opening 124 of the pole plate 102 for mechanically fixing the pole piece 126 to the
pole plate 102. A centrally located passage 131 extends through the pole piece 126. A pushpin
132 is movably supported in the passage 131.
[0025] A ferromagnetic armature 138 is disposed between the cap 104 and the pole piece
126. A bushing 140 guides the armature 138 within the bobbin 112. The armature 138 is
movable toward the pole piece 126 under the influence of an electromagnetic flux generated by
a pulse of current flowing through the coil 108 in one direction. This flux drives the armature 138
against the pushpin 132 to move the valve member 46 to the right as viewed in Figures 2-3 and
to one predetermined position. Furthermore, the armature 138 is movable away from the pole
piece 126 and toward the cap 104 (to the left as viewed in the Figures) under the influence of a
force generated in the opposite direction as will be described in greater detail below.
[0026] To this end, the pushpin 132 presents an enlarged head 142 which is disposed
adjacent one end of the poppet valve member 46 for contacting it when the armature 138 contacts
the pushpin 132.
[0027] While a particular electromagnetically actuated device has been described above,
the actuator employed with the valve assembly of the present invention may be of any known type
used in pneumatic valves such as a self-latching electromagnetic solenoid of the type described
in U.S. Patent No. 6,129,115 issued on October 10, 2000. Alternatively, the actuator may be an
electromagnetic solenoid having a floating armature with lost-motion biasing such as described
in prior art U.S. Patent Nos. 4,438,418 or 3,538,954. Each of these patents are assigned to the
assignee of the present invention and the disclosures of these patents are incorporated herein by
reference. Thus, those having ordinary skill in the art will appreciate from the description that
follows that the exact form of the actuator, whether electromagnetic or otherwise, forms no part
of the present invention. It should be further appreciated from the description of the invention
that follows that, although the preferred embodiment of the pneumatic valve assembly 10 of the
present invention is depicted as a three-way valve in Figures 1-3, the present invention may also
be alternately embodied in the form of a two-way valve (not shown), a four-way valve (as shown
in Figure 4-5), or the like.
[0028] When the valve member 46 has been moved by the solenoid assembly 14 to the
right as illustrated in Figure 3, the valve element 56 is moved into sealing engagement with the
valve seat 86 defined on the terminal end 51 of the end retainer 50. In this operative disposition,
fluid communication between the inlet port 30 and the cylinder port 32 is established and
pneumatic pressure may be delivered to any down stream device. However, when the valve
member 46 is in this operative disposition, frictional and adhesive forces may be generated at the
interface between the valve member 46 and the central bore openings 74, 76 of the end retainers
48, 50. These forces act to resist the biasing force generated in the opposite direction by the
biasing member 66 once the solenoid assembly 14 has been de-energized. Thus, these forces act
to degrade the speed and efficiency at which the valve member 46 is returned to its first position.
In addition, a reduction in the size of the biasing member 66 may result in a reduction of the force
generated thereby resulting in a slower valve response time.
[0029] In order to overcome this problem, the valve assembly 10 of the present invention
includes an air-assist passage, generally indicated at 94. In the embodiment illustrated in Figures
1-3, the air assist passage 94 is formed within the valve member 46 and provides fluid
communication between at least one cylinder port 32 and the recess 68 in the valve head 62 of the
valve member 46. Thus, the air assist passage 94 provides selective fluid communication between
the source of pressurized air and the recess 68. More specifically, and as illustrated in Figures 2
and 3, the air assist passage 94 includes an inlet portion 96 and a main passage 98. The inlet
portion 96 extends radially relative to the centerline "A" of the valve member. In this
representative embodiment, the inlet portion 96 is formed between valve elements 54, 56 and
between the valve seats 84, 86 defined in the valve bore 36. The main passage 98 provides fluid
communication between the inlet portion 96 and the recess 68. In this representative embodiment,
the main passage 98 is coaxial relative to the longitudinal axis A of the valve member.
[0030] The air-assist passage 94 provides a source of pneumatic pressure from the
pressurized cylinder port 32 that acts in combination with the biasing member 66 to operatively
move the valve member 46 in a direction opposite to the movement induced by the actuator 14.
Importantly, the air assist facilitates a faster acting valve. More specifically, a valve assembly 10
employing the air assist of the present invention may include a smaller biasing member 66 that
generates less force than would be required without the air assist. Because the biasing member
66 generates less force, the actuator 14 has less force to overcome and therefore moves the valve
member 46 to its first position faster. In addition, the biasing member 66, along with the air assist
provided through the passage 94, will be able to quickly and efficiently move the valve member
46 away from its second, or energized, position once the solenoid assembly 14 is de-energized.
The air-assist passage 94 provides the necessary mechanical impetus to assist in moving the valve
member 46 to the de-energized position.
[0031J Thus, the directly operated valve assembly of the present invention overcomes the
shortcoming and drawbacks of conventional valve assemblies when they are so reduced in size
such that the biasing member 66 alone is of insufficient physical size and mechanical strength to
repeatedly, quickly, and efficiently overcome the inertia of the valve member 46 and/or exceed
the frictional adhesion forces acting at the interface between the valve member 46 and the central
bore openings 74 and 76 of the end retainer 48, 50. This allows a very fast acting valve assembly
10 to be constructed in sizes below the conventional standards.
[0032] Referring now to Figures 4-5, an alternate, non-limiting embodiment of a directly
operated valve assembly having an air assist return of the present invention is generally indicated
at 210, where like numerals increased by 200 with respect to the embodiment illustrated in Figures
1-3 are used to designate like structure . The valve assembly 210 illustrated in Figures 4 and 5
includes a valve body 212 having a pressurized fluid inlet port 230 for communicating with a
source of pressurized fluid, such as air. Furthermore, the valve body 212 includes at least one
cylinder passage, or outlet port 232, that is adapted for fluid communication with one or more
pneumatically actuated devices. A valve bore 236 extends axially through the valve body 212.
In the embodiment illustrated here, the pneumatic valve assembly 210 is a four-way valve and
includes a pair of outlet ports 232, 234 and a pair of exhaust ports 238, 240 each in fluid
communication with the valve bore 236. The outlet ports 232, 234 are formed through the top
surface 216 of the valve body 212 opposite the inlet port 230 and exhaust ports 238, 240, which
are formed through the bottom surface 218. However, those having ordinary skill in the art will
appreciate that the inlet port 230, outlet and exhaust ports 232, 234 and 238, 240, respectively,
may be formed through the various surfaces of the valve body 212. For example, these ports may
all be formed through one surface, such as the bottom 218 of the valve body 212, without
departing from the scope of the invention. The inlet port 230, outlet and exhaust ports 232, 234
and 238, 240, respectively may also be threaded to accommodate any mechanism necessary to
establish fluid communication with another element that is operatively associated with the valve
assembly 210.
[0033] In the preferred embodiment illustrated in Figures 4-5, the valve bore 236 may
extend completely through the valve body 212 to present a pair of open ends 242, 244. A valve
member, generally indicated at 246, is movably supported within the valve bore 236 between
predetermined positions to selectively direct a flow of pressurized air from the inlet port 230
through the valve bore 236 to at least one of the outlet ports 232, 234. Concomitantly, the valve
member 246 may also selectively direct pressurized air to vent from at least one of the outlet ports
232, 234 to at least one of the exhaust ports 238, 240, as will be described in greater detail below.
A pair of end retainer inserts, generally indicated at 248 and 250, are received in the pair of open
ends 242, 244 of the valve body 212, thereby retaining the valve member 246 within the valve
bore 236 as will be described in greater detail below. Similarly, the valve assembly 210 may
include one or more inner retainers that are threadably positioned within the valve bore 236. In
the embodiment illustrated herein, the valve assembly 210 includes one inner retainer 251 that is
threadably positionable within the valve bore 236 as will be described in greater detail below.
[0034] The valve member 246 further includes a pair of opposed valve heads 260, 262
disposed at either end of the valve member 246 and at least one valve element formed on the valve
member 246 between the valve heads 260, 262. In the specific embodiment illustrated in Figures
4 and 5, a plurality of valve elements 252, 254, 256, and 258 are formed on the valve member 246
and are each operable to selectively direct a flow of pressurized air from an inlet port 230 through
the valve bore 236 to the respective outlet ports 238, 240. As shown in Figures 4 and 5, the valve
member 246 further includes annular grooves 270 that receive o-ring type seals 272, which
slidingly engage the central bore openings 274, 276 respectively, of the retainer inserts 248, 250
to prevent leakage of the pressurized air within the valve bore 236. In the preferred embodiment,
the valve member 246 is an aluminum insert that is over-molded with a suitable resilient material
such as rubber, or any known elastomer, in the appropriate places. More specifically, it should
be appreciated by those having ordinary skill in the art that the material of the sealing surface may
be made of any known composition that is slightly yielding, yet highly resilient, such as nitrile,
which may be bonded, or over-molded to the valve element 246. However, from the description
that follows, those having ordinary skill in the art will appreciate that the present invention is not
limited in any way to use in connection with the specific valve illustrated in Figures 4-5. Rather,
the present invention may be employed in connection with any other directly operated valve
including, but not limited to, for example, spool valves, flat rubber poppet valves, flapper valves,
pilot valves, or valve assemblies employed adjacent to or remote from the pneumatically actuated
device.
[0035] The end retainer inserts 248 and 250 each include a plurality of cylinder passages
264 defined in the diameter of the retainers that spaced radially relative to one another. The
cylinder passages 264 provide fluid communication between the valve bore 236 and the respective
adjacent ports. A biasing member 266, such as a coiled spring, is positioned between the cup-
shaped end retainer insert 250 and a recess 268 formed in one of the opposed valve heads 262 of
the valve member 246. The return spring 266 applies a constant biasing force against the valve
member 246 and to the left as viewed in Figures 4 and 5.
[0036] A plurality of valve seats 282, 284, 286, and 288 are presented in the valve bore
236. The valve seats 282, 284, 286, and 288 cooperate with the valve elements 252, 254, 256,
and 258, respectively, to seal the various passages in the valve body 212 as will be discussed in
greater detail below. The valve seats 282, 284, 286, and 288 provide a sealing contact with the
valve sealing surfaces of the valve elements 252, 254, 256, and 258 when the valve member 246
is in a closed position, relative to a particular outlet port, thereby interrupting the flow of
pressurized air to that port.
[0037] Of the plurality of valve seats 282, 284, 286, and 288 shown in Figures 4 and 5,
some may be formed directly in the valve bore 236 itself, as in the case of valve seat 284, while
others (e.g., valve seats 282, 286, and 288) may be disposed upon the end retainer inserts 248,
250 and inner retainer 251. The retainer inserts 248, 250, and 251 may be adjustably positioned
within the valve bore 236 of the valve body 212, having a threadable interaction with the ends
242, 244 or any other suitable portion of the valve bore 236. As discussed above, each of the
retainer inserts 248, 250 has a central bore 274, 276 that receives the opposed heads 260, 262 of
the valve member 246 and allows it to slidingly move within the valve body 212. Thus, the
threadably set position of the end retainer inserts 248, 250 within the valve body 212 controls the
sealing of the valve seats with a given force applied to the valve member 246. The end retainer
inserts 248, 250 further include annular grooves 291 and 293 which receive o-ring type seals 295
to prevent leakage of the pressurized air within the valve bore 236. On the other hand, the
positions to which the inner retainer insert 251 is threadably set defines the predetermined "open"
and "closed" positions of the valve assembly 210 and thereby sets the stroke length of the valve
member 246. And like the end retainer inserts, the inner retainer 251 may also include an annular
groove 297 which is adapted to receive an o-ring type seal 299 so as to prevent leakage of the
pressurized air within the valve bore 236.
[0038] In the preferred embodiment, the central bore 274 of retainer insert 248, which
receives the end 260 of the valve member 246 also extends fully through the retainer allowing the
actuator assembly 214 to engage and thereby actuate the valve member 246. As shown for
illustration purposes only, this may be accomplished by the use of an actuator pushpin 332 having
an enlarged head 342 that extends into the retainer insert 248 to engage and actuate the valve
member 246. As alluded to above, it should be appreciated by those of ordinary skill in the art that
the specific actuating means used to provide motive force to the valve member 246 lies beyond
the scope of the present invention. Accordingly, it should be further appreciated that any number
of different types of actuating elements, rather than a push pin, may be employed based on the
actuating means used. The actuator assembly 214, as previously mentioned, is used to selectively
actuate the valve member 246 within the valve bore 236 in the direction opposite to the biasing
force of the biasing member 266. In this manner, the actuator assembly 214 drives the valve
member to the right, as shown in Figure 4, and the biasing member 266 returns the valve member
246 to its original position (to the left, in Figure 5) when the actuator assembly 214 is deactivated.
[0039] When the valve member 246 has been moved by the solenoid assembly 214 to the
right as illustrated in Figure 4, the valve element 256 is moved into sealing engagement with the
valve seat 286 defined on the inner retainer 251. In this operative disposition, fluid
communication between the inlet port 230 and the cylinder port 232 is established and pneumatic
pressure may be delivered to any down stream device. However, when the valve member 246 is
in this operative disposition, rrictional and adhesive forces may be generated at the interface
between the valve element 256 and valve seat 286. These forces act to resist the biasing force
generated in the opposite direction by the biasing member 266 once the solenoid assembly 214
has been de-energized. Thus, these forces act to degrade the speed and efficiency at which the
valve member 246 is returned to its first position.
[0040] In order to overcome this problem, an air-assist passage, generally indicated at
294, is formed within the valve member 246 and extends between at least one cylinder port 232
and the recess 268 in the valve head 262 of the valve member 246 to provide selective fluid
communication between the source of pressurized air and the recess 294. More specifically, and
as illustrated in Figures 4 and 5, the air assist passage 294 includes an inlet portion 296 and a main
passage 298. The inlet portion 296 extends radially relative to the centerline A of the valve
member. In this representative embodiment, the inlet portion 296 is formed between a pair of
valve elements 252, 254. The main passage 298 provides fluid communication between the inlet
portion 296 and the recess 268 formed in the head 262 of the valve member 246. In this
representative embodiment, the main passage 298 is coaxial relative to the longitudinal axis A of
the valve member 246.
[0041] The air-assist passage 294 provides a source of pneumatic pressure from the
pressurized cylinder port 232 that acts in combination with the biasing member 266 to operatively
move the valve member 246 in a direction opposite to the movement induced by the actuator 214.
Importantly, the air assist facilitates a faster acting valve. More specifically, the valve assembly
210 employing the air assist of the present invention may include a smaller biasing member 266
that generates less force than would be required without the air assist. Because the biasing
member 266 generates less force, the actuator 214 has less force to overcome and therefore
moves the valve member 246 to its first position faster. In addition, the biasing member 266,
along with the air assist provided through the passage 294, will be able to quickly and efficiently
move the valve member 246 away from its second, or energized, position once the solenoid
assembly 214 is de-energized. The air-assist passage 294 provides the necessary mechanical
impetus to assist in moving the valve member 246 to the de-energized position.
[0042] Thus, the directly operated valve assembly of the present invention overcomes the
shortcoming and drawbacks of conventional valve assemblies when they are so reduced in size
such that the biasing member 266 alone is of insufficient physical size and mechanical strength to
repeatedly, quickly, and efficiently overcome the inertia of the valve member 246 and/or exceed
the factional adhesion forces acting at the interface of the valve member 246 and the central bore
openings 274 and 276 of the end retainer inserts 248, 250. This allows a very fast acting valve
assembly 210 to be constructed in sizes below the conventional standards.
[0043] Referring now to Figures 6, another, alternate non-limiting embodiment of a
directly operated valve assembly having an air assist return of the present invention is generally
indicated at 310, where like numerals increased by 300 with respect to the embodiment illustrated
in Figures 1-3 are used to designate like parts. More specifically, the valve assembly 310
illustrated here is also a three-way valve and includes many of the same or similar components of
the type described in connection with the three- and four-way valves illustrated in Figures 1-5.
Accordingly, those having ordinary skill in the art will appreciate that the following description
is presented in such a way so as to highlight the salient features of the present invention and does
not include a restatement of the discussion of all like components of the valve assembly of the type
described above.
[0044] With this in mind, the valve assembly 310 includes a valve body 312 having a
pressurized fluid inlet port 330 for communicating with a source of pressurized fluid, such as air.
A valve bore 336 extends axially within the valve body 312. The valve body 312 also includes
a cylinder port 332 and an exhaust port 338 both in fluid communication with the valve bore 336.
A valve member 346 is moveably supported within the valve bore 336 and has a pair of opposed
heads 360, 362. In addition, the valve member 346 includes at least one valve element 354, 356
that is operable to selectively direct a flow of pressurized air from the inlet port 330 through the
valve bore 336 to either the cylinder port 332 or the exhaust port 338. A plurality of valve seats
384, 386 are presented in the valve bore 336. The valve seats 384 and 386 cooperate with the
valve element 354, 356 to seal the various passages in the valve body 312 as will be described in
greater detail below. The valve seats 384, 386 provide sealing contact with the valve sealing
surfaces of the valve elements 354, 356 when the valve member 346 is in a closed position relative
to a particular port thereby interrupting the flow of pressurized air in that port.
[0045] Unlike the open ended valve bores illustrated in Figures 1-5, the valve bore 336
is a blind bore having an open end 342 and a closed end 344. An electromagnetic actuator, such
as a solenoid assembly, generally indicated at 314, is mounted to the valve body 312 at the open
end 342 of the valve bore 336. The solenoid assembly 14 acts to bias the valve member 346 in
one direction in the same manner as described with respect to the embodiments illustrated in
Figures 1-5. On the other hand, a biasing member 366, such as a coiled spring, is positioned
between the blind end 344 of the valve bore 336 and a recess 368 formed in one of the opposed
valve heads 362 of the valve member 346. The return spring 366 applies a constant biasing force
against the valve member 346 in a direction opposite to the force applied by the solenoid assembly
314.
[0046] When the valve member 346 has been moved by the solenoid assembly 314
downwardly, relative to Figure 6, the valve element 356 is moved into sealing engagement with
the valve seat 386 defined in the valve bore 336. In this operative disposition, fluid
communication between the inlet port 330 and the cylinder port 332 is established and pneumatic
pressure may be delivered to any downstream device. However, when the valve member 346 is
in this operative disposition, frictional and adhesive forces may be generated at the interface
between the seals 372 on the valve member 246 and the ends 342, 344 of the central bore 336.
These forces act to resist the biasing force generated in the opposite direction by the biasing
member 366 once the solenoid assembly 314 has been de-energized. As noted above, these forces
act to degrade the speed and efficiency at which the valve member 346 is returned to its first
position.
[0047] In order to overcome this problem, an air assist passage, generally indicated at
394, is formed within the valve body 312 and provides fluid communication between the cylinder
port 332 and the recess 368 in the valve head 362 of the valve member 346. Thus, the air assist
passage 394 provides selective fluid communication between the source of pressurized air and the
recess 368. However, those having ordinary skill in the art will note that the air assist passage
394 differs from the air assist passages 94 and 294 in that it is defined within the valve body 312
as opposed to the valve member 46, 246. More specifically, and as illustrated in Figure 6, the air
assist passage 394 includes an inlet portion 396 and a main passage 398. The inlet portion 396
extends axially within the valve body 312 relative to the movement of the valve member 346 and
provides fluid communication between the cylinder port 332 and the main passage 398. On the
other hand, and in this representative embodiment, the main passage 398 extends transverse to
the longitudinal axis A of the valve member 346 and provides fluid communication between the
inlet portion 396 and the recess 368 formed in the valve head 362 of the valve member 346.
[0048] The air-assist passage 394 provides a source of pneumatic pressure from the
pressurized cylinder port 332 that acts in combination with the biasing member 366 to operatively
move the valve member 346 in a direction opposite to the movement induced by the actuator 314.
Importantly, the air assist facilitates a faster acting valve. More specifically, a valve assembly 310
employing the air assist of the present invention may include a smaller biasing member 366 that
generates less force than would be required without the air assist. Because the biasing member
366 generates less force, the actuator 314 has less force to overcome and therefore moves the
valve member 346 to its first position faster. In this way, the biasing member 366, along with the
air assist provided through the passage 394, will be able to quickly and efficiently move the valve
member 346 away from its energized, position once the solenoid assembly 314 is de-energized.
The air-assist passage 394 provides the necessary mechanical impetus to assist in moving the
valve member 346 to the de-energized position. Thus, the directly operated valve assembly of the
present invention overcomes the shortcoming and drawbacks of conventional valve assemblies
when they are so reduced in size such that the biasing member 366 alone is of insufficient physical
size and mechanical strength to repeatedly, quickly, and efficiently overcome the inertia of the
valve member 346 and/or exceed the frictional adhesion forces acting between the valve member
346 and the valve bore 336. This allows a very fast acting valve assembly 310 to be constructed
in sizes below the conventional standards.
OPERATION
[0049] The operation of the directly operated pneumatic valve having an air assist return
of the present invention will now be described with reference to the three-way valve assembly 10
illustrated in Figures 1-3. However, those having ordinary skill in the art will appreciate that the
explanation of the operation of the valve illustrated in Figures 1-3 also applies with respect to the
four-way valve illustrated in Figures 4 and 5 as well as the three-way valve illustrated in Figure
6 and any other directly operated pneumatic valve that employs the air assist return of the present
invention.
[0050] In operation, pressurized air is supplied to the inlet port 30. The pressurized air
flows past a filter 31 disposed in that port and into the valve bore 36. When the solenoid
assembly 14 is de-energized, the biasing member 66 biases the valve member 46 to the left as
viewed in Figure 2 such that the valve element 54 is in sealing engagement with the valve seat 84.
In this disposition, the valve element 56 is disposed spaced from the valve element 86 providing
a flow passage between the cylinder port 32 and the valve bore 36. In this way, the cylinder port
32 is vented through the main valve bore 36 and the cylinder passages 64 and into the exhaust
port 38.
[0051] On the other hand, when the solenoid assembly 14 is energized, it produces a force
that drives the valve member 46 to the right as viewed in Figure 3 and against the biasing force
of the biasing member 66. In this operative disposition, the valve element 54 is moved off of the
valve seat 84 and the valve element 56 is quickly moved into sealing engagement with the valve
seat 86. Pressurized air is then allowed to flow through the inlet port 30, past the filter 31, into
the valve bore 36, past the open valve element 54 and valve seat 84, and into the cylinder port 32.
On the other hand, the interaction of the valve element 56 and valve element 86 seals the cylinder
port 32 with respect to the exhaust port 38. In addition, the air assist passage 94 is open to the
pressurized air flowing through the valve bore 36 and cylinder port 32. Thus, the recess 68
formed in the valve head 62 is similarly pressurized. However, the force generated by the
solenoid assembly 14 is sufficient to overcome the oppositely directed force generated by this
pressure.
[0052] Once the solenoid assembly 14 is de-energized and the actuating force is removed
from the valve head 60 of the valve member 46, the biasing member 66 and the air pressure acting
on the valve head 62 cooperatively start to move the valve member 46 back to its first position.
As this occurs, the valve element 56 that formed a seal in the energized position with the valve
seat 86 will quickly move off valve seat 86, so that the cylinder port 32 that was pressurized (and
providing the air-assist pressure) vents through the exhaust port 38. The valve member 46 is then
moved to the left until the valve element 54 seals with the valve seat 84 and fluid communication
between the cylinder port 32 and the exhaust port 38 is established past the valve element 56 and
the valve seat 86 through the valve bore 36. It should be noted that, once the valve member 46
is moving and any frictional or adhesion forces acting at the valve element 56 are overcome, the
biasing member 66 has enough mechanical strength to continue to move the valve member 46 to
its first de-energized position and the air-assist is no longer needed.
[0053] The air-assist passage provides a source of pneumatic pressure from the
pressurized cylinder port that acts in combination with the biasing member to operatively move
the valve member in a direction opposite to the movement induced by the actuator. Importantly,
the air assist facilitates a faster acting valve. More specifically, valve assemblies employing the
air assist of the present invention may include a smaller biasing member that generates less force
than would be required without the air assist. Because the biasing member generates less force,
the actuator has less force to overcome and therefore moves the valve member to its first position
faster. The biasing member, along with the air assist provided through the passage, will be able
to quickly and efficiently move the valve member away from its second, or energized, position
once the solenoid assembly is de-energized. The air-assist passage provides the necessary
mechanical impetus to assist in moving the valve member to the de-energized position. Thus, the
directly operated valve assembly of the present invention overcomes the shortcoming and
drawbacks of conventional valve assemblies when they are so reduced in size such that the biasing
member alone is of insufficient physical size and mechanical strength to repeatedly, quickly, and
efficiently overcome the inertia of the valve member and/or exceed the frictional adhesion forces
acting between the valve member and the central bore.
[0054] The structure of the direct operated valve assembly 10, 210, and 310 of the
present invention as described above has distinct advantages over the valves known in the related
art. The valve assemblies 10, 210, and 310 are very fast acting. Further, the size limitations of
convention valve assemblies are overcome and a range of smaller size valves become available.
More specifically, the air-assist passage allows for a very fast acting valve assembly in a size
much smaller than conventional designs. Thus, it is easily employed in environments where space
is at a premium. The small size of the pneumatic valve of the present invention is facilitated by
the air-assist passage providing a supplemental force of pressurized air to the biasing member.
Furthermore, and from the foregoing description, those having ordinary skill in the art will readily
appreciate that the air assist passage may be formed anywhere, either within the valve body, the
valve member, partially exterior of the valve body, or any combination of these to provide a
source of pneumatic pressure that acts in combination with the biasing member to operatively
move the valve member in the direction opposite to the movement induced by the actuator.
[0055] Once again, from the foregoing description, those having ordinary skill in the art
will appreciate that the present invention is not limited in any way to use in connection with a
poppet valve. Rather, the present invention may be employed in connection with any other
directly operated valve including, but not limited to, for example, spool valves, flat rubber poppet
valves, flapper valves, pilot valves, or valve assemblies employed adjacent to or remote from the
pneumatically actuated device.
[0056] The invention has been described in an illustrative manner. It is to be understood
that the terminology that has been used is intended to be in the nature of words of description
rather than of limitation. Many modifications and variations of the invention are possible in light
of the above teachings. Therefore, within the scope of the appended claims, the invention may
be practiced other than as specifically described.
WE CLAIM :
----------------
1. A directly operated valve assembly comprising!
a valve body having a pressurized air supply inlet port
in communication with a source of pressurized air, and at
least one cylinder port;
a valve bore extending axially within said valve body;
a valve member supported within said valve bore and
positionable only between a first position and a
predetermined second position within said valve bore to
selectively direct pressurized air from said inlet port
through said at least one cylinder port in said second
positiont said valve member comprising a pair of opposed
valve heads, at least one of said opposed valve heads having
a recess;
an actuator mounted to said valve body for moving said
valve in a first direction to said second position and a
biasing member disposed within said recess between said
valve member and said valve body adapted to provide a
biasing force to said valve member in an opposite second
direction to move said valve member to said first position;
and
an air-assist passage providing a source of pneumatic
pressure that acts in combination with said biasing member
to operatively move said valve member in said second
direction opposite to the movemement induced by said
actuator, said air assist passage providing communication
between said at least one cylider port and said source of
pressurized air* said air-assist passage having s
an inlet portion and a main passage, said inlet portion
extending radially relative to the center line A of the
valve member and providing fluid communication with said at
least one cylinder port* and said main passage providing
fluid communication between said inlet port and said recess;
and
wherein said inlet portion is formed between a pair of
valve elements commonly over-molded with rubber on said
valve member.
2. A directly operated valve assembly (10, 210, 310) as
claimed in claim 1 wherein said valve member (46, 246, 346)
comprises a pair of opposed valve heads (60, 62, 260, 262, 360,
362), at least one of said opposed valve heads having a recess
(68, 268, 368), said biasing member (66, 266, 366) operatively
disposed within said recess between said valve member (46, 246,
346) and said valve body (12, 212, 312).
3. A directly operated valve assembly (10, 210) as claimed
in claim 2 wherein said air-assist passage (94, 294) is formed
within said valve member (12, 212) and extends between said at
least one cylinder port (32, 232) and said recess (68, 268) in
said at least one opposed valve head (62, 262) of said valve
member to provide selective fluid communication between said
source of pressurized air and said recess (68, 268).
4. A directly operated valve assembly (10, 210) as claimed
in claim 3 wherein said air assist passage (94, 294) comprises an
inlet portion (96, 296) and a main passage (98, 298), said inlet
portion (96, 296) extemding radially relative to the center line
A of the valve member (46, 246) and providing fluid communication
with said at least one cylinder port (32, 232), and said main
passage (98, 298) providing fluid communication between said
inlet port and said recess (68, 268).
5. A directly operated valve assembly (10, 210) as claimed
in claim 4 wherein said main passage (98, 298) extends coaxially
within said valve member (46, 246) relative to the longitudinal
axis of the valve member.
6. A directly operated valve assembly (10) as claimed in
claim 4 wherein said inlet portion (96) is formed between a pair
of valve elements (54, 56) formed on said valve member (46).
7. A directly operated valve assembly (310) as claimed in
claim 2 wherein said air assist passage (394) is formed within
said valve body (312) and extends between said at least one
cylinder port (332) and said recess (368) in said valve head
(362) of said valve member (346) to provide selective fluid
communication between said source of pressurized air and said
recess (368).
8. A directly operated valve assembly (310) as claimed in
claim 7 wherein said air assist passage (394) comprises an inlet
portion (396) and a main passage (398), said inlet portion (396)
extending axially within said valve body (312) relative to the
movement of said valve member (346) within said valve bore (336)
and provides fluid communication between said said at least one
cylinder port (332) and said main passage (398)» said main
passage (398) extending transversely relative to the longitudinal
axis A of said valve member (346) and provides fluid
communication between said inlet portion (396) and said recess
(368) formed in said valve head (362) of said valve member (346).
9. A directly operated valve assembly (10, 210) as claimed
in claim 1 wherein said valve bore (46, 246) extends through said
valve body (12, 212) to present a pair of open ends (42, 44,
242, 244) and said assembly comprises a pair of retainer
assemblies (48, 50, 248, 250) threadably received in said pair of
open ends of valve body (12, 212) to close same.
10. A directly operated valve assembly (10, 210) as claimed
in claim 9 wherein each of said pair of retainer assemblies (48,
50, 248, 250) defines an innermost terminal end, said valve
member (46, 246) defining a poppet valve having a pair of opposed
annular valve heads ( 60, 62, 260, 262) disposed at either end of
said poppet valve, each of said pair of opposed valve heads
defining an outer diameter moveably received in sealing
engagement with said innermost terminal ends of said pair of
retainer assemblies (48, SO, 248, 250).
11. A directly operated valve assembly (210) as claimed in
claim 1 wherein said valve body (212) comprises a pair of
cylinder ports (232, 234) and a pair of exhaust ports (238, 240)
each in fluid communication with said valve bore (236), said
valve bore having a plurality of valve seats (282, 284,286, 288),
said valve member (246) comprises a plurality of valve elements
(252, 254,256, 258) defined along its lenght, said valve elements
cooperating with said valve seats to direct fluid from said valve
bore (236) through various ones of said pair of cylinder ports
(232, 234) and said pair of exhaust ports (23, 240).
12. A directly operated valve assembly (10, 210) comprising!
a valve body (12, 212) having a pressurized air supply inlet
port (30, 230) in communication with a source of pressurized air
and at least one cylinder port (32, 232);
a valve bore (36, 236) extending axially within said valve
body (12, 212);
a valve member (46, 246) having a pair opposed valve heads
(60, 62, 260, 262) slidingly disposed within said valve bore (36,
236) and movable between predetermined first and second positions
within said valve bore to selectively direct pressurized air from
said inlet port (30, 230) through said at least one cylinder port
(32, 232)?
an actuator (14, 214) disposed upon said valve body (12,
212) at one end (60, 260) of said valve member for moving said
valve member (46, 246) in one direction from said first to said
second position;
a biasing member (66, 266) disposed at the other end (62,
262) of said valve member between said valve member (46, 246) and
said valve body (12, 212) adapted to providing a biasing force to
said valve member; and
an air-assist passage (94, 294) disposed within said valve
member (46, 246) providing fluid communication between said
biased end (623, 262) of said valve member and the source of
pressurized air such that pneumatic pressure acts in combination
with said biasing member (66, 266) to operatively move said valve
member (46, 246) in a direction opposite to the movement produced
by said actuator (14, 214) and from said second to said first
position.
13. A directly operated valve assembly (10, 210) as claimed
in claim 12 wherein at least one of said opposed valve heads
(62, 262) comprises a recess (68, 268) said air assist
passage (94, 294) comprises an inlet portion (96, 296) and a main
passage (98, 298), said inlet portion (96, 296) extending
radially relative to the center line A of said valve member (46,
246) and providing fluid communication with said at least one
cylinder port (32, 232), and said main passage (98, 298)
providing fluid commmunication between said inlet portion (96,
296) and said recess (68, 268).
14. A directly operated valve assembly (10, 210) as claimed
in claim 13 wherein said main passage (96, 296) extends
coaxially within said valve member (46, 246) relative to the
longitudinal axis of the valve member.
15. A directly operated valve assembly (10) as claimed in
claim 13 wherein said inlet portion is formed between a pair of
valve elements (54, 56) formed on said valve member (46).
16. A directly operated valve assembly (310) comprising :
a valve body (312) having a pressurized air supply inlet
port (330) in communication with a source of pressurized air and
at least one cylinder port (332);
a valve bore (336) extending axially within said valve body
(312)5
a valve member (346) having a pair of opposed valve heads
(360, 362) slidingly disposed within said valve bore (336) and
movable between predetermined first and second positions within
said valve bore to selectively direct pressurized air from said
inlet port (330) through said at least one cylinder port (332);
an actuator (314) disposed upon said valve body (312) at one
end of said valve member for moving said valve member (346) in one
-direction from said first to said second position}
a biasing member (366) disposed at the other end of said
valve member between said valve member (346) and said valve body
(312) adapted in providing a biasing force to said valve member;
and
an air assist passage (394) formed within said valve body
(312) and extending between said at least one cylinder port (332)
and one of said pair of opposed valve heads (362) to provide
selective fluid communication between said source of pressurized
air and said valve head (362).
17. A directly operated valve assembly (310) as claimed in
claim 16 wherein said valve member(346)comprises a recess 268
formed in at least one valve head 362, said air assist passage
(394) comprises an inlet portion (396) and a main passage (398)»
said inlet portion (396) extending axially within said valve body
(312) relative to the movement of said valve member within said
valve bore and provides fluid communication between said at
least one cylinder port (332) and said main passage (398), said
main passage (398) extending traversely relative to the
longitudinal axis of said valve member (346) and provides fluid
communication between said inlet portion (330) and said recess
(368) formed in said valve head (362) of said valve member (346).

The invention relates to a directly operated valve assembly
comprising a valve body having a pressurized air supply inlet
port in communication with a source of pressurized air, and at
least one cylinder port; a valve bore extending axially within
said valve body; a valve member supported within said valve bore
and positionable only betrween a first position and a
predetermined second position within said valve bore to
selectively direct pressurized air from said inlet port through
said at least one cylinder port in said second position, said
valve member comprising a pair of opposed valve heads, at least
one of said opposed valve heads having a recess; an actuator
mounted to said valve body for moving said valve member in a
first direction to said second position and a biasing member
disposed within said recess between said valve member and said
valve body adapted to provide a biasing force to said valve
member in an opposite second direction to move said valve member
to said first position; and an air—assist passage providing a
source of pneumatic pressure that acts in combination with said

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Patent Number

272928

Indian Patent Application Number

622/CAL/2002

PG Journal Number

19/2016

Publication Date

06-May-2016

Grant Date

03-May-2016

Date of Filing

05-Nov-2002

Name of Patentee

MAC VALVES INC.

Applicant Address

30569 BECK 111 WIXON, MICHIGAN 48393

Inventors:

#	Inventor's Name	Inventor's Address
1	NEFF ROBERT	1052 WADDINGTON, BLOOMFIELD VILLAGE, MICHIGAN 48301

PCT International Classification Number

E03C 1/00

PCT International Application Number

N/A

PCT International Filing date

PCT Conventions:

#	PCT Application Number	Date of Convention	Priority Country
1	10/150,291	2002-05-17	U.S.A.