BRPI0503882B1 - "VALVES TO CONTROL A PRESSURED FLUID, DIRECTLY OPERATED VALVE ASSEMBLY AND METHOD OF CONTROLING THE FUNCTIONS OF A DIRECTLY OPERATED VALVE ASSEMBLY" - Google Patents

Description

(54) Title: VALVES TO CONTROL A PRESSURIZED FLUID, DIRECTLY OPERATED VALVE ASSEMBLY AND METHOD OF CONTROLLING THE FUNCTIONS OF A DIRECTLY OPERATED VALVE ASSEMBLY (73) Owner: MAC VALVES, INC. Address: 30569 Beck Road, P.O. Box 111, Wixom, Michigan 48393, UNITED STATES OF AMERICA (US) (72) Inventor: ROBERT H. NEFF; ERIC P. JANSSEN; LYNN R. LONG

Validity Term: 10 (ten) years from 10/02/2018, subject to legal conditions

Issued on: 10/02/2018

Digitally signed by:

Liane Elizabeth Caldeira Lage

Director of Patents, Computer Programs and Topographies of Integrated Circuits

1/22 “VALVE TO CONTROL A PRESSURIZED FLUID, AND METHOD OF CONTROLLING THE FUNCTIONS OF A VALVE SET DIRECTLY OPERATED”

Field of the Invention [0001] The present invention relates generally to pneumatic valve assemblies and more specifically to a directly operated pneumatic valve.

Background of the Invention [0002] Pneumatic valves directly operated, or actuated, are well known in the art for controlling the flow of pressurized air through them. Directly operated valves can be used alone or in conjunction with, for example, reel valves and regulators that, in turn, control the flow of pressurized air to and from various pneumatically driven devices such as pressure clutches, pneumatic brakes, devices classifiers or any other pneumatic device or application requiring exact control of operational air. Directly operated two-way, three-way, four-way and five-way valve assemblies are commonly employed in these environments. The valves concerned may include a valve body having a flow passage formed in the valve body. A valve member is supported within the flow passage and can be moved from one position to another in direct response to an operating force applied to the valve member by a servomotor. A plurality of orifices are used to connect the valve assembly with a system feed pressure as well as the various devices that the valve can control. The servomotor is typically an electromagnetically operated solenoid that is excited to move the valve member to a predetermined position within the flow passage. A return spring is often employed to bring the valve member back to an inactive position

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2/22 known. Valves of this type are used in a wide variety of operating environments where high flow rates and fast response times are desired.

[0003] As the technology for these valves has progressed, there has been an increase in the demand for valves designed for operating media with increasingly smaller physical dimensions. In addition, the valves in question must be capable of operating with time very fast cycle times. However, in the past, certain construction obstacles have exceeded the degree to which the valve assembly could be reduced while simultaneously increasing its speed. When the valve member and the flow passage are reduced below a predetermined dimension, the return spring may be of insufficient physical strength and mechanical strength to overcome the inertia of the valve member. In addition, after the valve member has been forced in one direction by the servomotor, frictional forces and surface adhesion can accumulate at the interface of the valve member seals and the flow passage. These frictional forces and the associated surface adhesion can act to inhibit the displacement of the valve member in the return direction which reduces the valve speed and therefore increases the response time of the valve. If the return spring is unable to provide sufficient propelling force to quickly or effectively move the valve member from its active position and return it to the inactive position when the servomotor force is removed, accurate control of the active device is lost. To overcome this deficiency, several construction strategies have emerged. However, the construction strategies proposed in the associated technique all suffer from the disadvantage of adding additional mechanisms or hardware or requiring remote valve assembly.

[0004] For example, a building strategy proposed in the related technique involves using dual electromagnetic servomotors to move

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3/22 the valve members in opposite directions. Thus, the return spring is replaced by an electromagnetic servomotor such as a solenoid. This solution, however, increases the complexity and cost of a second solenoid and the associated components, and also creates another dimensional biting factor. Individual electromagnetic servomotors that are activated in both directions have also been proposed by the correlated technique. However, these individual electromagnetic servomotors require a bulky double wound servomotor as well as additional electronic circuits and controls and are therefore typically mounted in a remote position in relation to the pneumatically operated devices they control. Remotely located valves negate the target of providing valves mounted in very close proximity to active devices. Such valves must be interconnected via ducts or other flow passages that require additional hardware and piping and can lower pneumatic efficiencies and introduce nail losses into the system.

[0005] Directly operated valves having directly mounted solenoid servomotors have been developed that offer a bypass flow part via a bypass opening in the valve member to assist the return spring to overcome frictional forces and associated surface adhesion. An example of a valve of this type is presented in patent application US SN 10/150 291 entitled DIRECTLY OPERATED PNEUMATIC VALVE HAVING AN AIR ASSIST RETURN, assigned to the assignee of the present invention, the exhibition of which is incorporated herein by reference. This bypass flow construction is effective, but it requires complex machining of the bypass openings that burden the cost of the valve. There is therefore a need for a more simplified directly operated valve construction.

Summary of the Invention [0006] A pneumatic valve directly operated having an action of

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4/22 differential auxiliary return of the present invention provides a directly operated valve assembly that eliminates bypass flow holes. More specifically, the directly operated valve assembly includes a valve body having a pressurized air supply inlet opening in communication with a pressurized air source, and a cylinder opening. A flow passage extends axially within the valve body, and a valve member is movably supported within the flow passage between predetermined positions to selectively direct pressurized air from the intake opening through the cylinder opening. A servomotor is mounted on the valve body to directly move the valve member in a first direction. A propensing member is opposed to the servomotor and positioned between the valve member and the valve body.

[0007] The valve member includes heads with different head diameters that sit against valve seats in the flow passage that also differ in diameter. The fluid pressure acting on different areas that result from the difference between the head and seat diameters provide different operating conditions. When the valve servomotor is deactivated, fluid pressure forces are balanced and the propelling member offers sufficient force to retain the valve member in a closed position. When the valve servomotor is activated and the valve member moves from the closed position, pressure forces acting on the different areas resulting from the different diameters of the valve member result in an unbalanced condition; The unbalanced pressure forces plus the force of the compressed propensing device creates an effective return force to operatively move the valve member in a direction opposite to the movement induced by the servomotor when the servomotor is deactivated.

[0008] The directly operated valve assembly of the present invention

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5/22 has distinct advantages. The pneumatic pressure acting on areas of seat and flow passages having different diameters generates a differential in forces acting on the valve member. In particular, pneumatic pressure acting in one direction over the area of a larger diameter valve member positioned within a first larger sealing area of the flow passage in combination with the pneumatic pressure simultaneously working in an opposite direction over a pressure head. valve member of smaller diameter positioned within a second area of smaller seat of the flow passage assists the propensity member to operatively move the valve member in a direction opposite to the movement induced by the servomotor. The operating speed of pneumatic valves of the present invention is approximately equal to that of valves using only a large return spring or valves provided with a return spring plus a bypass opening. The valve assemblies of the present invention eliminate the need for bypass airflow and therefore the complexity and cost of auxiliary bypass openings; The auto-return feature of the propelling member plus the force imbalance created by the geometry of the valve member heads and the flow-through seat areas quickly and efficiently pull the valve member out of its activated position once the servomotor is deactivated . The pneumatically assisted auto-return feature provides the necessary pressure / force to help move the valve to the off position.

[0009] The directly operated valve assembly of the present invention offers advantages over conventional valve assemblies when they are significantly reduced in size. A valve assembly of the present invention provides rapid acceleration of the valve member when a propensing member alone is of insufficient physical size and mechanical strength to repeatedly, quickly, and

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6/22 efficiently overcome the inertia of the valve member and / or exceed the frictional adhesion forces acting on the flow passage. This allows very fast-acting valve assemblies to be constructed smaller than conventional standards and the use of high voltage solenoids or servomotors.

[00010] Other areas of applicability of the present invention will be evident from the continuation of the detailed description that follows. It should be understood that the detailed description and specific examples, while indicating the preferred embodiment of the invention, are proposed for purposes of illustration only and are not proposed to limit the scope of the invention. [00011] Short Description of the Drawings [00012] The present invention will be more fully understood from the detailed description and the attached drawings, in which:

Figure 1 is a perspective view of a directly operated valve assembly provided with an auto-return of the present invention;

Figure 2 is a side view partially in cross section of the valve assembly directly operated in Figure 1;

Figure 3 is a partial exploded cross-sectional view taken from Figure 2;

Figure 4 is a cross-sectional side view of the directly operated valve body part substantially shown in Figure 2, illustrating the position of the valve member when the solenoid is deactivated;

Figure 5 is a side view in cross section similar to Figure 3, illustrating the valve member positioned between the positions of the activated and deactivated solenoid;

Figure 6 is a cross-sectional side view of a directly operated valve body part substantially shown in Figure 2, illustrating the position of the valve member when the solenoid is

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Ί / 22 activated;

Figure 7 is a side elevation view partially in cross section of another preferred embodiment of a directly operated valve assembly of the present invention; and

Figure 8 is a diagram of the method steps for operating a directly operated valve assembly provided with a differential assistance of the present invention.

Detailed Description of the Preferred Modes [00013] The following description of the preferential modalities is merely typical in nature and is not proposed in any way to limit the invention, its application or uses.

[00014] Referring next to the figures where identical numerals are used to designate the structure across the entire figures in the drawing, a modality of a directly operated valve assembly of the present invention is generally indicated at 10 in figure 1. The assembly valve body 10 includes a valve body 12 and an electromagnetic servomotor 14 mounted on the valve body 12. The valve body 12 has a thin rectangular shape defining upper and lower surfaces 16, 18 respectively, a pair of opposite side surfaces 20, 22 extending between the upper and lower surfaces 16 and 18, and extreme surfaces 24, 26. In a preferred embodiment, the servomotor 14 is a solenoid assembly mounted on the extreme surface 24 of the valve body 12.

[00015] Referring to figures 2 and 3, the valve body 12 includes a pressurized fluid inlet opening 28 for communication with a source of pressurized fluid (not shown), such as air. The valve body 12 additionally includes at least one discharge opening comprising, in one case, an outlet opening 30 and a return opening 32. A valve orifice or flow passage 34 extends axially through the valve body 12. In the modability illustrated in figs.

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8/22

1-3, the directly operated valve assembly 10 is a three-way valve and includes inlet opening 28, outlet opening 30 and return opening 32 each in fluid communication with flow passage 34. In this embodiment, each of the intake opening 28, the outlet opening 30, and the return opening 32 are formed through the upper surface 16 of the valve body 12 in a dispensing style. However, those skilled in the art will appreciate that the various openings can be formed through several different surfaces of the valve body 12. These openings and passages can be divided between surfaces 16, 18, 20, and / or 22 without departing from the scope of the invention . Inlet opening 28, outlet opening 30 and return opening 32 also threaded to accommodate any mechanism necessary to establish fluid communication with another component that is operatively associated with valve assembly 10. For this purpose, the valve body 12 is adapted to be mounted on a distributor, sub-base, or any one of a number of several pneumatically controlled devices (not shown).

[00016] As shown in figures 2-3, the flow passage 34 extends completely through the valve body 12 to offer a pair of open ends 36,37. A valve member 38 is slidably displaceable between predetermined positions within the flow passage 34 to selectively direct pressurized air from the intake port 28 through the healthy port 30 and return port 2 as will be described in greater detail below. A first end retainer 40 and a second end retainer 41 are positioned within the flow passage 34 to reliably receive valve member 38.

[00017] In a preferred modability, the valve member 38 can be a trigger member that is supported inside the flow passage for an alternate stroke inside it to control the flow of fluid through the valve body 12. In the present modality , the valve member

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9/22 further includes opposing valve heads, including a first valve head 42 and a second valve head 43 disposed on either end of valve member 38. A valve seat element 44 is positioned on a projecting portion 45 of the valve member 38 between opposite valve heads 42, 43. The position of the valve seat element 44 operates to selectively direct either a flow of pressurized air from the intake port 28 through the flow passage 34 to the outlet opening 30 or to direct pressurized fluid from outlet opening 30 to return opening 32. The first end retainer 40 has a first orifice 46, and the second end retainer 41 has a second orifice 47, respectively, which receives the first valve head 42 and second valve head 43, respectively, and allow valve member 38 to slide slidably within valve body 12. Parts of first orifice 46 and second orifice 47 forms parts of flow passage 34. A sealing member 48 such as an O-ring is positioned between the first valve head 42 and the first end retainer 40 to establish a fluid seal between the inlet orifice 28 and the open end 36. No similar sealing member is required between the second valve head 43 and the second hole 47 of the second end retainer 41.

[00018] In one embodiment, the trigger valve member 38 is preferably an aluminum insert element overmolded in the wisdom part 45 and connected with rubber to create the valve sealing element 44, and ground in specific dimensions to form, for example, example first and second valve heads 42.43. However, from the description that follows, those skilled in the art will appreciate that the present invention is not limited to any form of use in connection with a trigger valve. Preferably, the present invention can be used in relation to any other valve directly operated including, but without estr

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10/22 limited, for example, to reel valves, flat rubber trigger valves, flapper valves, pilot valves, or valve assemblies employed adjacent to or away from the pneumatically operated device.

[00019] Each position, that is, an activated solenoid position and a disabled solenoid position for valve member 38, are shown in figure 2. The activated solenoid position is shown to the left of a longitudinal geometric axis 50 formed through of the flow passage 34 and the position of the deactivated solenoid is shown to the right of the longitudinal geometry axis 50. To reach the position of the activated solenoid, the valve member 38 moves in the direction of arrow A until the seat element 44 engages with a terminal end 52 of the second end retainer 41. In this position, a flow path is created between the inlet orifice 28 and the outlet orifice 30 through the flow passage 34. The flow from the inlet orifice 28 has its entrance in the return port 32 blocked by the seat element 44 to engage with the end end 52. To return to the deactivated solenoid position, valve member 38 moves in the direction of seven B to element d and seat 44 engages with a sealing point 54 created at a distal end of an annular valve body extension 56 extending into the flow passage 34. In the off position, a flow path is created between the outlet 30 and the return port 32 beyond the end end 52 to allow pressurized fluid to be vented through return port 32. In the off position, the flow from inlet port 28 is blocked from entering either outlet port 30 or return orifice 32 by seat element 44 engages with sealing point 54. [00020] As best seen in figure 2, in a preferred modality servo motor 14 is an electromagnetic solenoid provided as a solenoid assembly generically including a housing 58 mounted on

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11/22 extreme surface 24 of valve body 12. Servo motor 14 provides a pusher pin 60 that contacts the first valve head 42 of valve member 38 to direct valve member 38 in the activated direction of arrow A. The housing 58 additionally includes a polar plate 62 positioned adjacent to the extreme surface 24, a cap 64 positioned opposite polar plate 62 and a solenoid housing 66. Solenoid housing 66 supports a conductive wire coil 68, conventionally wound around a coil 70. The conductive wire is connected to an electrical current source via one or more conductive pins 72. The conductive pins 72 are connected with one or more electrical contacts 74 and with wires (not shown) extending to the current source. The direction of the electromagnetic force generated by the current through coil 68 is controllable by a control circuit (not shown).

[00021] The pusher pin 60 extends sliding through an opening in the polar plate 62. The polar plate 62 additionally includes a ferromagnetic pole 76. The pusher pin 60 contacts a ferromagnetic armature 78 disposed between the solenoid housing 66 and the top 64. The armature 78 and the pusher pin 60 move in the direction of the polar piece 76 under the influence of an electromagnetic flow generated by a pulse of the current passing through the coil 68 in one direction. This flow produces a driving force in an X direction that drives pusher pin 60 to move valve member 38 in the activated direction of solenoid A.

[00022] A total displacement of armature 78 in the direction of arrow C can be controlled in part using an adjusting device 80. In the illustrated embodiment, the adjusting device 80 is threaded with top 64 in such a way that a the movable end 82 contacts a distal end 84 of the armature 78 positioned opposite the pusher pin 60. By adjusting the screw engagement depth of the adjusting device 80, a total travel distance of the pin

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12/22 pusher 60 and valve member 38 between the off and on positions is predetermined.

[00023] Although a specific electromagnetic driven device has been described here, the servomotor 14 employed with the valve assembly of the present invention can be of any known type used for pneumatic valves. It should be further appreciated that although a preferred pneumatic valve assembly embodiment 10 of the present invention is represented as a three-way valve, the present invention can alternatively be incorporated in the form of a two-way, four-way or similar valve.

[00024] As best seen in figure 3, when valve member 38 is driven by pusher pin 60 to the activated solenoid position, a flow path D is provided between sealing point 54 and sealing element 44. O The displacement of the valve member 38 proceeds until the sealing element 44 engages with a sealing contact point 86 created on a sealing edge 88 of the end end 52. It is convenient to form the sealing edge 88 at an angle Θ with a face engaging 90 of the sealing element 44 in such a way that an annular point of contact is formed to create the valve seal. This is illustrated and described in US patent 6,668,861 (Wilbams), issued December 30, 2003, jointly assigned to the assignee of the present invention, the invention of which is incorporated herein by reference. In the activated solenoid position, fluid is prevented from overtaking the end end 52 between an outer perimeter 92 of the end end 52 and a projecting perimeter surface 94 of the valve body 12 by a first sealing member 96. In a preferred modality, the first sealing member 96 is an elastomeric O-ring. The first sealing member 96 is retained within a sealing groove 98 created at the end end 52. [00025] A propeller member 100 is positioned within a

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13/22 cavity 101 formed inside the second valve head 43 and acts both on a protrusion 102 created inside the second valve head 43 and on a surface 104 of the second extreme retainer 41. The propeller member 100 produces a propelling force represented by force Z arrows. The function of the propensing member 100 will be described in more detail below. In the illustrated modability, the propensing member 100 is a hebcoidal spring, however, those skilled in the art will appreciate that any propensity 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 skilled in the art will appreciate that, due to the sheer number of appropriate proponent members that can be employed in this environment, it is not efficient to try to catalog them all here. More precisely, it should be sufficient for purposes of description and illustration to mention that the member propensor 100 exhibits a constant upward force against valve member 38 as seen in figs. 2-5.

[00026] In the deactivated position of the solenoid (partially shown to the right of the longitudinal geometry axis 50 as seen in figure 3), a flow path E is created between the seating element 44 and the sealing edge 88 ,. The second end retainer 41 is substantially cabciform and includes a plurality of cylindrical passages 106 defined in the second end retainer 41 and spaced radially from each other. Cylindrical passages 106 provide fluid communication between flow passage 34 and respective adjacent orifices, for example to allow fluid flow between outlet port 30, via flow path E, to return port 32. In the deactivated position of the solenoid, fluid is prevented from escaping a threaded connection 108 between the second end retainer 41 and the valve body 12, as well as between an outer perimeter 110 adjacent to the end end 52 and a projecting annular surface 112 of the valve body 12 , by a second sealing member 114. Similar to the

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14/22 first sealing member 96, in a preferred embodiment the second sealing member 114 is an elastomeric O-ring. The second sealing member 114 is retained within a second sealing groove 116 positioned on the second end retainer 41 between the sealing groove 98 and the threaded connection 108.

[00027] Figure 3 further illustrates that the seating point 54 forms a first annular seal having a diameter F. The sealing contact point 86 of the sealing edge 88 forms a second annular seal having a diameter G. In addition, the second hole 47 of the second end retainer 41 has a diameter Ή. The diameter G is substantially equal to the diameter Ή. The diameter F is larger than both diameters G and Ή for reasons that will be described in more detail below.

[00028] Referring to both figures 3 and 4, so that the valve member 38 moves from the deactivated position of the solenoid to the activated position (or in the reverse direction), the fluid in cavity 101 or in a second cavity 117 adjacent to the open end 36 must be moved. For this purpose, a valve compensation passage 118 (only partially shown in figure 3) is provided. In addition, a free gap 120 is provided between the second orifice 47 of the second end retainer 41 and a cylindrical outer surface 122 adjacent to a distal end 124 of the second valve head 43. The fluid is therefore displaced between the cavity 101 and either the open end 36 or return port 32 via the valve compensation passage 120 to allow the valve member 38 to move longitudinally within the flow passage 34.

[00029] Figure 4 shows the deactivated solenoid position of valve member 38 where servomotor 14 is deactivated. In this position, flow path E is open and a second engaging face 128 of the

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15/22 seating element 44 is in contact with seating point 54 of the valve body extension 56. The seating path 54 of the valve body extension 56. The flow path E between the outlet port 30 and the return port 32 remains open until armature 78 is activated. The flow path E is open between the engaging face 90 of the seating element 44 and the sealing contact point 86 of the sealing edge 88. The flow path E also includes a recess 130 created adjacent to the second valve head 43 valve member 38. The recess 130 communicates with the plurality of cylindrical passages 106 to complete a fluid flow path. To reach the deactivated solenoid position, the fluid in the second cavity 117 travels into the cavity 101 through the valve compensation passage 118 when the valve member 38 moves in the direction of the arrow Β. The pressurized fluid in the inlet port 28 is isolated from both the outlet port 30 and the return port 32. Pressurized fluid in the inlet port 28 is prevented from leaking into the second cavity 117 by the sealing member 48 as previously exposed.

[00030] Referring generally to figure 5, an intermediate position of valve member 38 is shown. In the intermediate position, the armature 78 has just been activated causing the pusher pin 60 to start repositioning the valve member 38 in such a way that the second engaging face 128 of the seating element 44 is no longer in contact with the seating point 54 valve body extension 56. Both flow paths D and E are open. The engaging face 90 of the seating element 44 is not yet in contact with the sealing contact point 86 of the sealing edge 88. The fluid in the cavity 101 moves into the second cavity 117 through the pressure compensation passage. valve 118.

[00031] Referring to figure 6, the activated solenoid position

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16/22 of valve member 38 is shown. In this position, the flow path D is open and the engaging face 90 of the seating element 44 is in contact with the sealing contact point 86 of the sealing edge 88, closing the flow path Ε. Propensing member 100 is compressed by the force provided by armature 78 through pusher pin 60. Flow path D between inlet orifice 28 and outlet orifice 30 remains open until armature 78 is deactivated. The fluid in cavity 101 moved into the second cavity 117 via the valve compensation passage 118. The pressurized fluid in the inlet port 28 is prevented from leaking into the second cavity 117 by the sealing member 48 disposed inside of a third sealing groove 132. The sealing member 48 forms a seal between an inner cylindrical wall 134 having an orifice diameter J of the first end retainer 40 and an outer perimeter wall 136 of the first valve head 42. The diameter of hole J is substantially equal to the diameter F of the seating point 54.

[00032] Figure 6 also identifies an adjustable feature for the second end retainer 41. A depth K measured from the end surface 26 to the end end 52 of the second end retainer 41 is controlled progressively by adjusting the screw connection 108. By controlling the depth K, the position of the sealing edge 88 is controlled. A displacement 138 of the seating element 44 of the valve member 38 between the seating point 54 and the sealing contact point 86 is thereby controlled, which can be used to vary the valve cycle time, the total fluid volume. discharged by valve assembly 10, etc.

[00033] The operation of the valve assembly 10 is now described below with reference to the preceding figures. Referring again to fig. 4, the valve assembly 10 is initially deactivated and the valve member 38 is therefore positioned in the deactivated position. Fluid

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17/22 pressurized in the inlet port 28 acts on an area 140 in an upward direction of M-force sets as shown in figure 4. Area 140 is the remaining area of the first valve head 42 after subtracting a diameter L from the member diameter 38 of the first valve head 42 (Area 140 = 7t ((JL) / 2) ² ). Simultaneously, pressurized fluid in the intake port 28 acts on an effective area 142 in a downward direction of the force arrows N as shown in figure 4. Area 142 is the remaining area of the second coupling face 128 delimited at the seating point 54 after subtracting the diameter L of valve member 38 from diameter F (Area 142 - 7t ((FL) / 2) ² ). Because diameters J and F are substantially equal, area 140 substantially equal to area 142 and balanced forces (Μ = N) are acting on valve member 38 in this position. Propensing member 100 is therefore required, applying a compressive force to keep second engaging member 128 in contact with seating point 54 and creating a seal between inlet port 28 and outlet port 30 (as well as return point 32).

[00034] Referring generally to figures 2 to 6 inclusive, when the fluid pressure is balanced through valve member 38 in the deactivated position, armature 78 of servomotor 14 only to overcome the propensing force Z of propensing member 100 and any frictional / adherent force of the sealing member 48 to initiate the displacement of the valve member 38. When armature 78 is activated, its X force accumulates until it is sufficient to overcome the propensitive force Z and the frictional / adhesion force of the member seal 48. The following valve member 38 begins to move. As shown in figure 5, after the valve member 38 travels a sufficient distance to create a gap (flow path D) between the second engagement face 128 and the seating point 54, the valve member 38 is no longer balanced in pressure.

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18/22 [00035] As soon as flow path D is created, fluid pressure begins to build up in recess 130 and against a surface 144 of the second valve head 43. An area 146 of surface 144 is the remaining area of the second valve head 43 after subtracting the diameter R from valve member 38 from diameter Ή (Area 146 = 7t ((HR) / 2) ² ). The free gap 120 between the second valve head 43 and the second orifice 47 is ignored for this calculation due to its minimal effect on the resulting force differential. A diameter V of the second valve head 43 is therefore treated for the purposes of this analysis. as substantially equal to the diameter Ή. A resulting force S acts on area 146 which is oppositely directed but smaller than force M, because the diameter J is larger than diameters Ή or V (area 140> area 146). A pressure imbalance (MS) is therefore created which is oppositely directed in relation to the force of solenoid X. However, because valve member 38 is already in motion at this time and the force of solenoid X is continuing to build up as as armature 78 approaches pole piece 76, valve member 38 rapidly accelerates. [00036] In the intermediate position shown in figure 5, both flow paths D and E are open. The fluidic pressure forces acting on the seating element 44 are presumably substantially balanced. Small effects of differential pressure of the fluid flow through the outlet and return ports 30, 32 are ignored.

[00037] Referring to both figures 3 and 6, when the engaging face 90 of the seating element 44 contacts the sealing contact point 86, the solenoid force X and the momentum of the valve member 38 compresses the coupling face 90 against the sealing contact point 86 and part of the sealing edge 88. Due to the clearance of the seating area provided by the angle Θ (figure 3), the pressure acts on only a part of the coupling face 90 In this position, an effective or resultant force T is created

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19/22 that opposes the fluid force Μ. The force T results from the pressure acting on the engaging face 90 of the seating element 44 over an area 148. Area 148 is the remaining area of the seating element 44 deburred in the extension of the sealing contact point 86 after subtracting the diameter L of valve member 38 of diameter G (Area 148 - 7t ((GL) / 2) ² ). An effective return force U tending to retake valve member 38 in an upward direction (opposing the solenoid force X) results from the difference between force M and force T (U = (MT)). When a combination of the compressive strength of the sealing edge 88 at the sealing contact point 86, the propelling force of the propelling member 100 and the effective return force U are equal to the solenoid force X, the movement of the valve member 38 stops. This produces the activated position of the valve assembly 10. The pressure in the inlet port 28 and the outlet port 30 is now blocked by return port 32.

[00038] On this occasion, three forces exist that are available to quickly return valve member 38 to the deactivated position. First, the thrust member 100 is compressed, further increasing the thrust force Z. Second, a compressive force Y is temporarily generated when the seating element 44 compresses against the sealing contact point 86 and sealing edge 88. Third, the thrust force effective return U acts to resume valve member 38 in the disabled return direction of arrow B.

[00039] When armature 78 is subsequently deactivated, valve member 38 begins to move rapidly due to the above three forces. The valve member 38 is stopped when the second engagement face 128 taps and compresses against the seating point 54. Because the diameter F and the diameter J are the same, the balanced pressure condition for the valve member 38 is restored and the valve member 38 stops moving when the compressive strength of the second coupling face 128 is

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20/22 equal to the bias force Z of the bias member 100. The pressure in the outlet port 30 is subsequently dissipated through the return port 32 via flow path E or through an open outlet port 30.

[00040] Figure 7 identifies another embodiment of the present invention having different orifice positions than those shown in figure 2. Figure 7 represents one of a pluritude of alternative configurations for the valve orifices of the present invention. In figure 7, a valve assembly 150 includes a valve body 152 having a servomotor 14 mounted thereon. An outlet orifice 154 similar to outlet orifice 30 is positioned in the left direction similar to that shown in figure 2. An inlet orifice 156 is positioned to the right as seen in figure 8 or opposite inlet 28 shown in figure 2. One return port 158 is directed towards the observer in figure 7. Valve member 38 is not shown for clarity.

[00041] Referring to figure 8, a method for operating a valve assembly of the present invention includes the steps of reliably supporting a valve member within a flow passage having a first sealing diameter in which a first valve part is in contact with a valve servomotor (160); generating a driving force with the valve servomotor to directly move the valve member in a first direction (162); and providing a second sealing diameter that is smaller than the first sealing diameter and the first valve part in which a pluridity of forces acting on the valve member results in an operable effective return force to assist in moving the valve member in one second direction opposite the first direction with the elimination of the driving force (164).

[00042] In a preferred modability of the valve of the present invention, the materials are as follows. The valve body 12 is constructed of die-cast aluminum. The valve member 38 is of a metal such as

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21/22 aluminum. The first extreme seal 40 is made of a low friction polymeric material such as DELRIN®. The second end member 41, which provides a sliding fit but is not relied upon for a rough seal, is a brass material. The valve seat element 44 is made of a rubber or rubbery material such as Buna-N having a durometer of approximately 80 to 90. Propensing member 100 is made of spring steel. These materials are merely typical, as the identified materials do not imply the invention or its applications.

[00043] The operation of a valve of the present invention is described with reference to the inlet fluid pressure acting on the valve member and sealing diameters In addition to the forces and flow paths described here, a part of the inlet pressure of the valve also it can partially dissipate through the outlet and / or return orifices when the valve member is repositioned, and a small back pressure can be generated. The backpressures and / or forces of the fluid inside the cavity 101 acting against the stem 102, and extremly acting against the distal end 124 when fluid is transferred through the valve equalization passage 118 are considered negligible.

[00044] A directly operated pneumatic valve having a differential assisted return of the present invention offers several advantages. A pressure balanced condition of the valve assembly exists when the valve servomotor is deactivated. This means that less force is required by the valve servomotor to start the valve member travel and the valve member can be accelerated very quickly. When the valve servomotor is activated and the valve member is positioned to allow flow, an unbalanced pressure condition is present. The pressure imbalance acting on different areas of the valve member is created by having different areas of the valve member head that engage with valve sealing areas of different areas.

Petition 870180066308, of 07/31/2018, p. 29/36

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The pressure imbalance acting on different areas of the valve member is created by having different areas of the valve member head that engage with valve sealing areas of different areas. The unbalanced pressure acts to accelerate the valve member more quickly when the servo motor is deactivated. A valve assembly of the present invention eliminates the need for a valve bypass port that reduces the cost of the valve.

[00045] The description of the invention is merely typical in nature and, thus, variations that do not depart from the core of the invention are proposed to fall within the scope of the invention. The variations in question should not be considered as an escape from the spirit and scope of the invention.

Petition 870180066308, of 07/31/2018, p. 30/36

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Claims (21)

1. Valve to control a pressurized fluid, characterized by the fact that it comprises: a valve body (12) including a fluid inlet port (28), an outlet port (30) and a flow port (34) in communication with both the inlet port (28) and the outlet port (30), the valve body (12) having a seating point (54) defining a first annular seal, the first annular seal having a first diameter (F); a first end retainer (41) positioned inside the flow passage (34), the first end retainer (41) has a seal contact point (86) defining a second annular seal, the second annular seal having a second diameter ( G), the first sealing diameter (F) larger than the second diameter (G); a valve member (38) having first and second heads (42, 43) being deshzantably positioned within the flow passage (34), the first valve head (42) having a first head diameter (J) defining a first head area (140) and a second head area (146) smaller than the first head area (140); and a seating element (44) disposed on the valve member (38) positionable to tap the first annular seal in a first position and to tap the second annular seal in a second position; wherein the valve member (38) is movable from the first position to the second position by a propelling force (X) applied in a first direction (A) and in the second position the pressurized fluid acts on both the first area of the head (140 ) and an area (148) of the seating element (44) generates a resulting return force (U) defined as a fluid force (M) subtracted from a force (T) acting on the area (148) of the operable seating element to drive the valve member (38) in a second direction (B) opposite the first direction Petition 870180066308, of 07/31/2018, p. 31/36 2/5 (A) with the cessation of the driving force (X). Valve according to claim 1, characterized by the fact that it further comprises a propensing member (100) positioned between the valve member (38) and the valve body (12) adapted to compel the valve member in the second direction and opposite the first direction. 3. Valve according to claim 2, characterized by the fact that it also comprises: a propelling force operatively created by the propelling member (100); where the sum of the propelling force and the effective return force (U) is less than the driving force Valve according to claim 1, characterized in that the valve body (12) further comprises a return port (32). Valve according to claim 4, characterized by the fact that it comprises a first spruce flow path between the outlet orifice (30) and the return port (32) operatively created in the first in the first position, in which the orifice inlet (28) is isolated from both the outlet and return port. Valve according to either of claims 4 or 5, characterized in that it comprises a second open flow path between the inlet port (28) and the outlet port (30) in the second position, in which the port return valve (32) is isolated from both the inlet and outlet ports. Valve according to any one of claims 1 to 6, characterized in that it further comprises an adjusting device (80) operable to progressively adjust a displacement of the valve member (38) between the first position and the second position. Valve according to any one of claims 1 to 7, characterized by the fact that it also comprises a second extreme retainer (41) positioned within the flow passage; where both the first (41) and the second (41) end retainers are operable to support Petition 870180066308, of 07/31/2018, p. 32/36 3/5 sliding the valve member (38). Valve according to claim 8, characterized by the fact that the first extreme retainer (41) comprises a screw connection adapted to detach the first extreme retainer with the valve body (12). Valve according to either of claims 8 or 9, characterized in that the second diameter is operatively created on the first end retainer (41) and is positioned within the flow passage (34) using the screw connection. Valve according to any one of claims 1 to 10, characterized in that the sealing element (44) is positioned between the first and second annular seals. Valve according to any one of claims 1 to 11, characterized in that the first annular seal comprises an annularly extended valve body extension within the flow passage (34). Valve according to any one of claims 1 to 12, characterized in that the first head diameter is equal to the first diameter. Valve according to any one of claims 1 to 13, characterized in that the second head diameter is equal to the second diameter. Valve according to any one of claims 1 to 14, characterized in that the area (148) of the seating element (44) is the remaining area of the seating element (44) limited to an extension of the contact point seal (86) after subtracting a valve member diameter (L) from the valve member (38) from the second diameter (G). 16. Method of controlling the functions of a directly operated valve assembly, the valve assembly having a valve servomotor Petition 870180066308, of 07/31/2018, p. 33/36 4/5 directly connected with a valve body (12), a flow passage (34) extending axially inside the valve body (38), a valve member including a first valve part, the flow passage having a first seal and a second seal diameter, characterized by the fact that it comprises: reliably support the valve member within the flow passage in which the first valve part contacts the valve servomotor; generate a driving force with the valve servomotor to directly move the valve member in a first direction; and establish the second sealing diameter smaller than the first sealing diameter and that the first valve part is characterized by the fact that a plurality of forces act on the valve member to result in an effective return force operable to assist in moving the valve. valve member in a second direction opposite to the first direction by removing the driving force. 17. Method according to claim 16, characterized in that it further comprises compelling the valve member (38) in the second direction. Method according to either of claims 16 or 17, characterized in that it further comprises reliably sealing the first valve head within the flow passage. Method according to any one of claims 16 to 18, characterized in that it further comprises extending a sealing member of the valve member (38) radially to position the first sealing diameter. 20. Method according to claim 19, characterized in that it further comprises positioning the sealing member between each of the first and second sealing diameters, in which the contact between the sealing member and the first sealing diameter creates a first member position Petition 870180066308, of 07/31/2018, p. 34/36 5/5 valve (38) and the contact between the sealing member and the second sealing diameter creates a second position of the valve member. 21. Method according to any one of claims 16 to 20, characterized in that it further comprises a second valve head with a smaller diameter than that of the first valve head in such a way that a differential force is created between the first and second valve head by a pressure acting on both valve heads. Petition 870180066308, of 07/31/2018, p. 35/36 2/8