WO2008157392A1 - 3-way high-pressure air operated valve - Google Patents

3-way high-pressure air operated valve Download PDF

Info

Publication number
WO2008157392A1
WO2008157392A1 PCT/US2008/066972 US2008066972W WO2008157392A1 WO 2008157392 A1 WO2008157392 A1 WO 2008157392A1 US 2008066972 W US2008066972 W US 2008066972W WO 2008157392 A1 WO2008157392 A1 WO 2008157392A1
Authority
WO
WIPO (PCT)
Prior art keywords
control element
reduced diameter
diameter portion
valve
ports
Prior art date
Application number
PCT/US2008/066972
Other languages
French (fr)
Inventor
Todd W. Larsen
Original Assignee
Tescom Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to CN2008800197826A priority Critical patent/CN101743420B/en
Priority to EP20080771065 priority patent/EP2165097B1/en
Priority to JP2010512394A priority patent/JP5580195B2/en
Priority to BRPI0812709 priority patent/BRPI0812709A2/en
Priority to CA2690099A priority patent/CA2690099C/en
Priority to MX2009013780A priority patent/MX2009013780A/en
Application filed by Tescom Corporation filed Critical Tescom Corporation
Priority to AT08771065T priority patent/ATE529674T1/en
Priority to RU2009147675/06A priority patent/RU2516049C2/en
Priority to KR1020107000845A priority patent/KR101496350B1/en
Priority to AU2008265997A priority patent/AU2008265997B2/en
Publication of WO2008157392A1 publication Critical patent/WO2008157392A1/en
Priority to NO20093430A priority patent/NO339246B1/en

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16KVALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/04Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only lift valves
    • F16K11/044Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only lift valves with movable valve members positioned between valve seats
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00Fluid handling
    • Y10T137/8593Systems
    • Y10T137/86493Multi-way valve unit
    • Y10T137/86549Selective reciprocation or rotation
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00Fluid handling
    • Y10T137/8593Systems
    • Y10T137/86493Multi-way valve unit
    • Y10T137/86574Supply and exhaust
    • Y10T137/86622Motor-operated
    • Y10T137/8663Fluid motor
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00Fluid handling
    • Y10T137/8593Systems
    • Y10T137/86493Multi-way valve unit
    • Y10T137/86574Supply and exhaust
    • Y10T137/8667Reciprocating valve
    • Y10T137/86686Plural disk or plug
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00Fluid handling
    • Y10T137/8593Systems
    • Y10T137/86493Multi-way valve unit
    • Y10T137/86879Reciprocating valve unit
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00Fluid handling
    • Y10T137/8593Systems
    • Y10T137/86493Multi-way valve unit
    • Y10T137/86879Reciprocating valve unit
    • Y10T137/86895Plural disk or plug

Definitions

  • the present invention generally relates to air-operated valves, and more particularly, to a high-pressure 3-way air-operated valve.
  • Plants and factories utilize process control devices to control the flow of fluids in processes, wherein "fluids” may include liquids, gases, or any mixture that can flow through a pipe.
  • Fluids may include liquids, gases, or any mixture that can flow through a pipe.
  • Manufacturing processes that create consumer articles or goods such as fuel, food, and clothes require control valves to control and regulate fluid flow.
  • Even a medium sized factory may utilize hundreds of control valves to control a process. Control valves have been utilized for over a century, during which time valve designers have continuously improved the operational performance of control valves.
  • a 2-way or bi-directional valve may not be sufficient to achieve the desired functionality for a selected part of the system. Accordingly, designers wishing to equip a process system with a 3-way functionality may opt to use two separate two-way or bi-directional valves plumbed together in the same system.
  • FIG. 1 is a top plan schematic view of a tri-directional or 3-way air-operated control valve in accordance with the present invention and illustrating an exemplary relative location of three ports.
  • Fig. 2 is a cross-sectional side view of one embodiment of the 3-way air- operated control valve taken along line 2-2 of Fig. 1 and assembled in accordance with the present invention and illustrating the control element in a first position.
  • FIG. 3 is another cross-sectional side view of the 3-way air-operated control valve taken along line 3-3 of Fig. 1.
  • Fig. 4 is a cross-sectional side view similar to Fig. 2 and illustrating the control element in a second position.
  • FIGs. 5A and 5B are schematic flow diagrams illustrating a first exemplary flow pattern with the control element in the first and second positions, respectively.
  • Figs. 6A and 6B are schematic flow diagrams illustrating a second exemplary flow pattern with the control element in the first and second positions, respectively.
  • Figs. 7A and 7B are schematic flow diagrams illustrating a third exemplary flow pattern with the control element in the first and second positions, respectively.
  • FIGs. 8A and 8B are schematic flow diagrams illustrating a fourth exemplary flow pattern with the control element in the first and second positions, respectively.
  • the control valve 10 generally includes a valve body 12, first through third ports 14, 16, and 18, and an actuator assembly 20 for controlling flow through the first through third ports 14, 16, and 18 in a manner to be explained in greater detail below.
  • One example of the relative positions of the ports 14, 16, and 18 is shown schematically in Fig. 1.
  • the first port 14 is disposed perpendicular to the second port 16, the second port 16 is disposed perpendicular to the third port 18, and the first and second ports 14 and 16 are disposed one hundred and eighty degrees from each other.
  • the actuator assembly 20 is operated by an air supply source 22 (shown schematically in Fig. 2).
  • the air supply source 22 is connected to a control or air supply port 24.
  • the actuator assembly 20 includes a control element 26, which can also be referred to as a thrust pin or control poppet, that is mounted within the valve body 12.
  • the control element 26 is disposed along an axis 1 that is perpendicular to each of the ports 14, 16, 18.
  • the control element 26 is adapted for movement or displacement along the axis 1 between a first position 26A illustrated in Figs. 2 and 3 and a second position 26B illustrated in Fig. 4.
  • the valve body 12 includes an internal bore or throat 28, which is sized to form a gap or clearance space 30 around the control element 26.
  • the throat 28 is adapted to be in fluid communication with each of the first through third ports 14, 16, 18.
  • the control element 26 moves in response to pressure changes at the air supply port 24, such that the control element 26 can shift between the first and second positions.
  • the valve body 12 further includes a central portion or base 32 having an upper part 34 and a lower part 36, with the throat 28 being formed by a bore 38 extending through the base 32.
  • the ports 14, 16, and 18 are formed in the base 32. More specifically, as shown in Figs. 2 and 3, the first port 14 comprises a generally linear passageway extending through the base 32 of the valve body 12, while the second and third ports 16, 18 include turns.
  • the second port 16 includes a first portion 16a, a second portion 16b, and a third portion 16c.
  • the third port 18 includes a first portion 18a, a second portion 18b, and a third portion 18c.
  • the second portions 16b, 18c of the second and third ports 16, 18 are disposed perpendicular to the first and second portions 16a, 16c, 18a, 18c.
  • the upper part 34 of the base 32 is sized to receive an upper valve insert 40, while the lower part 36 of the base 32 is sized to receive a lower valve insert 42.
  • the upper valve insert 40 and the upper part 34 of the base 32 are sized to form an upper chamber 44 in the throat 28, while the lower valve insert 42 and the lower part 36 of the base 32 are sized to form a lower chamber 46 in the throat 28.
  • the valve inserts 40 and 42 are constructed of 316 stainless steel.
  • the upper chamber 44 is in flow communication with the throat 28 when the control element 26 is in the lowered or second position as shown in Fig. 4, while the lower chamber 46 is in flow communication with the throat 28 when the control element 26 is in the raised or first position as shown in Figs. 2 and 3.
  • the first port 14 is in fluid communication with the throat 28 via a bore 48, which as described above is generally linear.
  • the second port 16 is in fluid communication with the upper chamber 44 via a bore 50, which as described above comprises the first, second, and third portions 16a, 16b, 16c of the second port 16.
  • the third port 18 is in fluid communication with the lower chamber 46 via a bore 52, which as described above includes the first, second, and third portions 18a, 18b, 18c of the third port 18.
  • the first port 14 can be brought into selective fluid communication with the second port 16 by placing the control element 26 in the second position of Fig. 4, or with the third port 18 by placing the control element 26 in the first position of Figs. 2 and 3.
  • the upper valve insert 40 is secured by an upper cap 54, while the lower valve insert 42 is secured by a lower cap 56.
  • the upper valve insert 40 includes an outer channel 58 having a seal 60 and a backup ring 62.
  • the lower valve insert 42 includes an outer channel 64 having a seal 66 and a backup ring 68.
  • the upper valve insert 40 includes a bore 70 sized to receive an upper portion 72 of the control element 26.
  • the upper portion 72 of the control element 26 includes a channel 74 sized to receive a seal 76 and a backup ring 76.
  • the lower valve insert 42 includes a bore 80 sized to receive a lower portion 82 of the control element 26.
  • the lower portion 82 includes a channel 84 sized to receive a seal 86 and a backup ring 88. Accordingly, the control element 26 is guided for shiftable sliding movement within the valve body 12 by the bores 70 and 80 in the respective valve inserts.
  • the backup rings preferably include a plastic ring sized and configured to maintain the position of the corresponding seals in the appropriate channels.
  • the actuator assembly 20 includes a piston 90 slidably disposed within a piston chamber 92 formed between the upper cap 54 and an upper portion 94 of the upper valve insert 40.
  • the piston chamber 92 is in flow communication with the air supply port 24, such that the piston 90 moves within the piston chamber 92 in response to pressure changes in a region 96 above the piston 90.
  • a lower portion 98 of the piston 90 is coupled to the upper portion 72 of the control element 26 by any suitable coupling.
  • an adjustable cap screw 100 disposed in a countersunk hole in the piston 90 secures the piston 90 to the control element.
  • the cap screw 100 may be covered by a removable cover 102. As spring 91 biases the piston 90 upwardly, which in turn biases the control element 26 toward the first position of Figs. 2 and 3.
  • the control element also includes a central portion 104 having a thickness or diameter which may be widened relative to the thickness or diameters of the upper and lower portions 72 and 82 of the control element 26.
  • the central portion 104 is bounded on both ends by tapered upper and lower seating surfaces 106 and 108.
  • the seating surfaces 106 and 108 are tapered, and further are preferably frustoconical. Each of the seating surfaces 106 and 108 transitions into a narrowed portion 110, 112, respectively.
  • the seating surface 106 is sized and positioned to seat against an upper valve seat 1 14 carried by the base 32 and surrounding a portion of the throat 28, while the seating surface 108 is sized and positioned to seat against an upper valve seat 116 carried by the base 32 and surrounding a portion of the throat 28.
  • the upper valve seat 114 is disposed between first port 14 and the third portion 16c of the second port 16.
  • the lower valve seat 116 is disposed between the first port 14 and the third portion 18c of the third port 18.
  • the first port 14 communicates with the throat 28 of the valve body 12 at a location between the upper and lower valve seats 114, 116.
  • the second port 16 communicates with the throat 28 at a location opposite the upper valve seat 1 14 from the first port 14.
  • the third port 18 communicates with the throat 28 at a location opposite the lower valve seat 116 from the first port 14.
  • the control element 26 includes another tapered portion 107 formed opposite the seating surface 106 on the other side of the narrowed portion 110.
  • the control element 26 includes yet another tapered portion 109 formed opposite the seating surface 108 from the narrowed portion 112.
  • the exposed area of the seating surface 106 equals the exposed area of the tapered portion 107. Accordingly, when the control element 26 is in the first position of Figs. 2 and 3, the pressure acting on the equal exposed areas is the same, and therefore the control element 26 is effectively balanced.
  • the control element 26 is in the second position of Fig. 4, once again the exposed area of the seating surface 108 equals the exposed area of the tapered portion 109.
  • the air supply port 24 preferably is threaded receiving a supply line (not shown) connected to a pneumatic supply.
  • the pneumatic supply may be, for example, a source of compressed shop-air supplied at a pressure of between approximately eighty (80) psig and approximately one-hundred and fifty (150) psig.
  • the force required to move the piston 90 is a function of the surface area of the piston 90.
  • the position of the control element 26 within the control valve 10 can be controlled by introducing compressed air into the piston cavity 92.
  • the spring 91 biases the piston 90 into the raised first position depicted in Figs. 2 and 3, which causes the seating surface 106 to sealingly engage the valve seat 114.
  • the introduction of compressed air into the region above the piston increases the pressure acting on the top of the piston 90.
  • the piston 90 and hence the control element 26 moves downward from the position shown in Figs. 2 and 3 to the position shown in Fig. 4. Accordingly, the seating surface 106 moves away from the seat 114, and the seating surface 108 moves into contact with the seat 116.
  • the ports 14, 16, 18, and the above-mentioned chambers and bores are arranged to define a first flow path designated PATH 1 Figs. 2 and 3) and a second flow path designated PATH 2 (Fig. 4).
  • PATH 1 extends through the port 14, the bore 48, the throat 28, between the seating surface 108 and the lower valve seat 116 (by virtue of the fact that the control element 26 is in the raised or first position), through the lower chamber 46, through the bore 52, and through the port 18.
  • at least the portions of the first flow path PATH 1 that extend through the ports 14 and 18 are disposed perpendicular to the axis 1 of the control element 26.
  • fluid may flow in different directions.
  • the pressures at one or more of the ports 14, 16 or 18 may rise to between approximately 10,000 psig and approximately 20,000 psig. It will be understood that, depending on which of the ports 14, 16, 18 is under pressure, the pressure will act on one of the tapered seating surfaces 106, 108 of the control element 26, and will urge the control element 26 upward or downward.
  • the valve 100 of the present invention may be operated with standard compressed shop-air delivered to the region of the piston 90 via the air supply port 24 at a pressure of between approximately eighty (80) psig and one-hundred and fifty (150) psig. Because the diameter of the piston 90 provides a much larger surface area than the exposed surface are of the seating surfaces 106 or 108, the relatively low- pressure shop air is sufficient to generate sufficient force to overcome the forces of the spring 91 or any upward force caused by fluid pressure in the process system. [0029J In accordance with the disclosed example, the control valve 10 may be used in the number of exemplary operational modes. A first exemplary operational mode is illustrated in Figs.
  • FIGs. 6A in which the control element 26 is in the first position
  • 6B in which the control element 26 is in the second position
  • Pressure is supplied to port 16, and the control valve 10 is effectively closed, as pressure would not flow to the other two ports 14 or 18.
  • the control element 26 is shifted to the second position, pressure will flow along the second flow path PATH 2 and flow between ports 16 and 14.
  • Port 18 is shut off.
  • the control element 26 returns to the first position, the flow is closed from port 16, but pressure in port 14 would flow into port 18.
  • port 18 is an exhaust port for port 14.
  • FIGs. 7A and 7B A third exemplary operational mode is illustrated in Figs. 7A (in which the control element 26 is in the first position) and 7B (in which the control element 26 is in the second position). Pressure is applied to port 18, such that pressure flows along PATH 1 from port 18 to port 14. When the control element 26 shifts to the second position, flow is shut off to port 14 from port 18, but flow is permitted from port 14 two ports 16. In this situation, port 16 is an exhaust port for port 14.
  • the examples of Figs. 6A, 6B, 7 A and 7B are both forms all of fill and dump valves (or exhaust three-way valves). Further, the example of Figs. 6A and 6B is a normally closed three-way valve, while the example of Figs. 7A and 7B is a normally open three-way valve.
  • FIGs, 8A in which the control element 26 is in the first position
  • 8B in which the control element 26 is in the second position
  • a supply is hooked up to port 16
  • another supply is hooked up to port 18.
  • each of the ports 14, 16, 18 have been disclosed herein as being perpendicular to the axis 1 of the control element 26, in alternative embodiments, one or more of the ports 14, 16, 18 can extend at generally any angle relative to the axis 1 of the control element 26.
  • control valve 10 for high-pressure applications
  • present valve 10 may also be adapted for use in pressure applications.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Lift Valve (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

A high pressure three-way control valve comprises a valve body defining first, second, and third ports disposed in selective fluid communication with each other via a control element. The control element is movable between a first seated position and a second seated position to selectively control the direction of fluid between the first and second port, or alternatively, between the first and third port. So configured, the control valve serves a function that conventionally requires two valves plumbed together.

Description

3- WAY HIGH-PRESSURE AIR OPERATED VALVE
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] The priority benefit of U.S. Provisional Patent Application No. 60/944,407, filed June 15, 2007 is hereby claimed, and the entire contents thereof are incorporated herein by reference.
FIELD OF THE INVENTION
[0002J The present invention generally relates to air-operated valves, and more particularly, to a high-pressure 3-way air-operated valve.
BACKGROUND
[0003] Plants and factories utilize process control devices to control the flow of fluids in processes, wherein "fluids" may include liquids, gases, or any mixture that can flow through a pipe. Manufacturing processes that create consumer articles or goods such as fuel, food, and clothes require control valves to control and regulate fluid flow. Even a medium sized factory may utilize hundreds of control valves to control a process. Control valves have been utilized for over a century, during which time valve designers have continuously improved the operational performance of control valves.
[0004] When designing a process, the designer is faced with many design requirements and design constraints. For example, some process control applications require a valve to enable flow in two directions, which are often called bi-directional flow valves. Another example of a design constraint includes the pressure at which the fluid will be operating within the process. For example, some processes operate at relatively low pressures, e.g., less than approximately 10,000 pounds per square inch gauge (psig), while other processes may operate at relatively high pressures, e.g., greater than 10,000 psig, and up to approximately 20,000 psig.
[0005] In certain circumstances, a 2-way or bi-directional valve may not be sufficient to achieve the desired functionality for a selected part of the system. Accordingly, designers wishing to equip a process system with a 3-way functionality may opt to use two separate two-way or bi-directional valves plumbed together in the same system.
BRIEF DESCRIPTION OF THE DRAWINGS
[0006] Fig. 1 is a top plan schematic view of a tri-directional or 3-way air-operated control valve in accordance with the present invention and illustrating an exemplary relative location of three ports.
[0007] Fig. 2 is a cross-sectional side view of one embodiment of the 3-way air- operated control valve taken along line 2-2 of Fig. 1 and assembled in accordance with the present invention and illustrating the control element in a first position.
[0008] Fig. 3 is another cross-sectional side view of the 3-way air-operated control valve taken along line 3-3 of Fig. 1.
[0009] Fig. 4 is a cross-sectional side view similar to Fig. 2 and illustrating the control element in a second position.
[0010] Figs. 5A and 5B are schematic flow diagrams illustrating a first exemplary flow pattern with the control element in the first and second positions, respectively.
[0011] Figs. 6A and 6B are schematic flow diagrams illustrating a second exemplary flow pattern with the control element in the first and second positions, respectively. [0012] Figs. 7A and 7B are schematic flow diagrams illustrating a third exemplary flow pattern with the control element in the first and second positions, respectively.
[0013] Figs. 8A and 8B are schematic flow diagrams illustrating a fourth exemplary flow pattern with the control element in the first and second positions, respectively.
DETAILED DESCRIPTION
[0014] Referring now to Figs. 1-4, an air-operated tri-directional or 3-way control valve 10 assembled in accordance with the teachings of the present invention is shown. The control valve 10 generally includes a valve body 12, first through third ports 14, 16, and 18, and an actuator assembly 20 for controlling flow through the first through third ports 14, 16, and 18 in a manner to be explained in greater detail below. One example of the relative positions of the ports 14, 16, and 18 is shown schematically in Fig. 1.
[0015] As depicted, the first port 14 is disposed perpendicular to the second port 16, the second port 16 is disposed perpendicular to the third port 18, and the first and second ports 14 and 16 are disposed one hundred and eighty degrees from each other. It will be understood that the relative positions of the ports 14, 16 and 18 may take any suitable form. The actuator assembly 20 is operated by an air supply source 22 (shown schematically in Fig. 2). The air supply source 22 is connected to a control or air supply port 24. The actuator assembly 20 includes a control element 26, which can also be referred to as a thrust pin or control poppet, that is mounted within the valve body 12. In the disclosed embodiment, the control element 26 is disposed along an axis 1 that is perpendicular to each of the ports 14, 16, 18. The control element 26 is adapted for movement or displacement along the axis 1 between a first position 26A illustrated in Figs. 2 and 3 and a second position 26B illustrated in Fig. 4.
[0016] The valve body 12 includes an internal bore or throat 28, which is sized to form a gap or clearance space 30 around the control element 26. The throat 28 is adapted to be in fluid communication with each of the first through third ports 14, 16, 18. As will be explained in greater detail below, the control element 26 moves in response to pressure changes at the air supply port 24, such that the control element 26 can shift between the first and second positions.
[0017] The valve body 12 further includes a central portion or base 32 having an upper part 34 and a lower part 36, with the throat 28 being formed by a bore 38 extending through the base 32. In the disclosed example, the ports 14, 16, and 18 are formed in the base 32. More specifically, as shown in Figs. 2 and 3, the first port 14 comprises a generally linear passageway extending through the base 32 of the valve body 12, while the second and third ports 16, 18 include turns. For example, the second port 16 includes a first portion 16a, a second portion 16b, and a third portion 16c. Similarly, the third port 18 includes a first portion 18a, a second portion 18b, and a third portion 18c. In the disclosed embodiment, the second portions 16b, 18c of the second and third ports 16, 18 are disposed perpendicular to the first and second portions 16a, 16c, 18a, 18c. Alternative embodiments, however, could be constructed differently.
[0018] The upper part 34 of the base 32 is sized to receive an upper valve insert 40, while the lower part 36 of the base 32 is sized to receive a lower valve insert 42. The upper valve insert 40 and the upper part 34 of the base 32 are sized to form an upper chamber 44 in the throat 28, while the lower valve insert 42 and the lower part 36 of the base 32 are sized to form a lower chamber 46 in the throat 28. Preferably, the valve inserts 40 and 42 are constructed of 316 stainless steel. The upper chamber 44 is in flow communication with the throat 28 when the control element 26 is in the lowered or second position as shown in Fig. 4, while the lower chamber 46 is in flow communication with the throat 28 when the control element 26 is in the raised or first position as shown in Figs. 2 and 3. In the disclosed example, the first port 14 is in fluid communication with the throat 28 via a bore 48, which as described above is generally linear. The second port 16 is in fluid communication with the upper chamber 44 via a bore 50, which as described above comprises the first, second, and third portions 16a, 16b, 16c of the second port 16. Finally, the third port 18 is in fluid communication with the lower chamber 46 via a bore 52, which as described above includes the first, second, and third portions 18a, 18b, 18c of the third port 18. In accordance with the disclosed example, the first port 14 can be brought into selective fluid communication with the second port 16 by placing the control element 26 in the second position of Fig. 4, or with the third port 18 by placing the control element 26 in the first position of Figs. 2 and 3.
[0019] The upper valve insert 40 is secured by an upper cap 54, while the lower valve insert 42 is secured by a lower cap 56. Preferably, the upper valve insert 40 includes an outer channel 58 having a seal 60 and a backup ring 62. Still preferably, the lower valve insert 42 includes an outer channel 64 having a seal 66 and a backup ring 68. The upper valve insert 40 includes a bore 70 sized to receive an upper portion 72 of the control element 26. Preferably, the upper portion 72 of the control element 26 includes a channel 74 sized to receive a seal 76 and a backup ring 76. Similarly, the lower valve insert 42 includes a bore 80 sized to receive a lower portion 82 of the control element 26. Preferably, the lower portion 82 includes a channel 84 sized to receive a seal 86 and a backup ring 88. Accordingly, the control element 26 is guided for shiftable sliding movement within the valve body 12 by the bores 70 and 80 in the respective valve inserts. The backup rings preferably include a plastic ring sized and configured to maintain the position of the corresponding seals in the appropriate channels.
[0020] In addition to the control element 26, the actuator assembly 20 includes a piston 90 slidably disposed within a piston chamber 92 formed between the upper cap 54 and an upper portion 94 of the upper valve insert 40. The piston chamber 92 is in flow communication with the air supply port 24, such that the piston 90 moves within the piston chamber 92 in response to pressure changes in a region 96 above the piston 90. A lower portion 98 of the piston 90 is coupled to the upper portion 72 of the control element 26 by any suitable coupling. In the disclosed example, an adjustable cap screw 100 disposed in a countersunk hole in the piston 90 secures the piston 90 to the control element. The cap screw 100 may be covered by a removable cover 102. As spring 91 biases the piston 90 upwardly, which in turn biases the control element 26 toward the first position of Figs. 2 and 3.
[0021] The control element also includes a central portion 104 having a thickness or diameter which may be widened relative to the thickness or diameters of the upper and lower portions 72 and 82 of the control element 26. The central portion 104 is bounded on both ends by tapered upper and lower seating surfaces 106 and 108. The seating surfaces 106 and 108 are tapered, and further are preferably frustoconical. Each of the seating surfaces 106 and 108 transitions into a narrowed portion 110, 112, respectively.
The seating surface 106 is sized and positioned to seat against an upper valve seat 1 14 carried by the base 32 and surrounding a portion of the throat 28, while the seating surface 108 is sized and positioned to seat against an upper valve seat 116 carried by the base 32 and surrounding a portion of the throat 28. In the disclosed embodiment, the upper valve seat 114 is disposed between first port 14 and the third portion 16c of the second port 16. Additionally, the lower valve seat 116 is disposed between the first port 14 and the third portion 18c of the third port 18. Said another way, the first port 14 communicates with the throat 28 of the valve body 12 at a location between the upper and lower valve seats 114, 116. The second port 16 communicates with the throat 28 at a location opposite the upper valve seat 1 14 from the first port 14. The third port 18 communicates with the throat 28 at a location opposite the lower valve seat 116 from the first port 14.
[0022] Still referring to Figs. 2-4, the control element 26 includes another tapered portion 107 formed opposite the seating surface 106 on the other side of the narrowed portion 110. Similarly, the control element 26 includes yet another tapered portion 109 formed opposite the seating surface 108 from the narrowed portion 112. In accordance with the disclosed example, the exposed area of the seating surface 106 equals the exposed area of the tapered portion 107. Accordingly, when the control element 26 is in the first position of Figs. 2 and 3, the pressure acting on the equal exposed areas is the same, and therefore the control element 26 is effectively balanced. When the control element 26 is in the second position of Fig. 4, once again the exposed area of the seating surface 108 equals the exposed area of the tapered portion 109. Consequently, the pressure acting on the equal exposed areas is the same. [0023] The air supply port 24 preferably is threaded receiving a supply line (not shown) connected to a pneumatic supply. The pneumatic supply may be, for example, a source of compressed shop-air supplied at a pressure of between approximately eighty (80) psig and approximately one-hundred and fifty (150) psig. The force required to move the piston 90 is a function of the surface area of the piston 90.
[0024] Based on the foregoing, it will be appreciated that the position of the control element 26 within the control valve 10 can be controlled by introducing compressed air into the piston cavity 92. For example, in the absence of compressed air supplied to the cavity 92, the spring 91 biases the piston 90 into the raised first position depicted in Figs. 2 and 3, which causes the seating surface 106 to sealingly engage the valve seat 114. However, the introduction of compressed air into the region above the piston increases the pressure acting on the top of the piston 90. When enough pressure is applied to overcome the biasing force of the spring 91, the piston 90 and hence the control element 26 moves downward from the position shown in Figs. 2 and 3 to the position shown in Fig. 4. Accordingly, the seating surface 106 moves away from the seat 114, and the seating surface 108 moves into contact with the seat 116.
[0025] It will be appreciated that the ports 14, 16, 18, and the above-mentioned chambers and bores are arranged to define a first flow path designated PATH 1 Figs. 2 and 3) and a second flow path designated PATH 2 (Fig. 4). As shown in Figs 2 and 3, PATH 1 extends through the port 14, the bore 48, the throat 28, between the seating surface 108 and the lower valve seat 116 (by virtue of the fact that the control element 26 is in the raised or first position), through the lower chamber 46, through the bore 52, and through the port 18. Accordingly, at least the portions of the first flow path PATH 1 that extend through the ports 14 and 18 are disposed perpendicular to the axis 1 of the control element 26. As will be explained in greater detail below, depending on which of the ports 14, 16, 18 are pressurized, fluid may flow in different directions.
[0026J Next, when the control element 26 is shifted to the lower or second position illustrated in Fig. 4, PATH 2 extends through the port 14, the bore 48, the throat 28, between the seating surface 106 and the upper valve seat 114 (by virtue of the fact that the control element 26 is now in the lowered or second position), through the upper chamber 44, through the bore 50, and through the port 16. Accordingly, at least the portions of the second flow path PATH 2 that extend through the ports 14 and 16 are disposed perpendicular to the axis 1 of the control element 26.
[0027] In high pressure applications, however, the pressures at one or more of the ports 14, 16 or 18 may rise to between approximately 10,000 psig and approximately 20,000 psig. It will be understood that, depending on which of the ports 14, 16, 18 is under pressure, the pressure will act on one of the tapered seating surfaces 106, 108 of the control element 26, and will urge the control element 26 upward or downward.
[0028] So configured, the valve 100 of the present invention may be operated with standard compressed shop-air delivered to the region of the piston 90 via the air supply port 24 at a pressure of between approximately eighty (80) psig and one-hundred and fifty (150) psig. Because the diameter of the piston 90 provides a much larger surface area than the exposed surface are of the seating surfaces 106 or 108, the relatively low- pressure shop air is sufficient to generate sufficient force to overcome the forces of the spring 91 or any upward force caused by fluid pressure in the process system. [0029J In accordance with the disclosed example, the control valve 10 may be used in the number of exemplary operational modes. A first exemplary operational mode is illustrated in Figs. 5A (in which the control element 26 is in the first position) and 5B (in which the control element 26 is in the second position). In Fig. 5A the port 14 is pressurized such that pressure flows through the control valve 10 along the first flow path PATH 1 and exits through the port 18. Port 16 is shut off. When the control element 26 shifts to the second position, pressure flows along PATH 2 from port 14 to port 16, with port 18 being shut off.
[0030] A second exemplary operational mode is illustrated in Figs. 6A (in which the control element 26 is in the first position) and 6B (in which the control element 26 is in the second position). Pressure is supplied to port 16, and the control valve 10 is effectively closed, as pressure would not flow to the other two ports 14 or 18. When the control element 26 is shifted to the second position, pressure will flow along the second flow path PATH 2 and flow between ports 16 and 14. Port 18 is shut off. When the control element 26 returns to the first position, the flow is closed from port 16, but pressure in port 14 would flow into port 18. In this case, port 18 is an exhaust port for port 14.
[0031] A third exemplary operational mode is illustrated in Figs. 7A (in which the control element 26 is in the first position) and 7B (in which the control element 26 is in the second position). Pressure is applied to port 18, such that pressure flows along PATH 1 from port 18 to port 14. When the control element 26 shifts to the second position, flow is shut off to port 14 from port 18, but flow is permitted from port 14 two ports 16. In this situation, port 16 is an exhaust port for port 14. The examples of Figs. 6A, 6B, 7 A and 7B are both forms all of fill and dump valves (or exhaust three-way valves). Further, the example of Figs. 6A and 6B is a normally closed three-way valve, while the example of Figs. 7A and 7B is a normally open three-way valve.
[0032] A fourth exemplary operational mode is illustrated in Figs, 8A (in which the control element 26 is in the first position) and 8B (in which the control element 26 is in the second position). A supply is hooked up to port 16, and another supply is hooked up to port 18. When the control element 26 is in the first position, flow goes from port 18 to port 14. Port 16 is closed. When the control element 26 shifts to the second position, flow goes from port 16 to port 14. Port 18 is closed.
[0033] While each of the ports 14, 16, 18 have been disclosed herein as being perpendicular to the axis 1 of the control element 26, in alternative embodiments, one or more of the ports 14, 16, 18 can extend at generally any angle relative to the axis 1 of the control element 26.
[0034] While the present disclosure has thus far included a description of a control valve 10 for high-pressure applications, the present valve 10 may also be adapted for use in pressure applications.
[0035] In light of the foregoing, it should be appreciated that the present detailed description provides merely an example of an air-operated bi-directional control valve constructed in accordance with the principles of the present invention. Variations and modifications, including variations in the materials utilized, that do not depart from the spirit and scope of the present invention are intended to be within the scope of the appended claims.

Claims

WHAT IS CLAIMED:
1. A high pressure fluid control device, comprising:
a valve body defining a first port, a second port, and a third port;
a throat disposed within the valve body and in fluid communication with each of the first, second, and third ports;
first and second valve seats mounted in the throat of the valve body;
a control element disposed within the throat of the valve body and having a first seating surface and a second seating surface, the control element movable between a first position in which the first seating surface is seated against the first valve seat and a second position in which the second seating surface is seated against the second valve seat; the first and second ports in fluid communication with one another via the throat along a second flow path when the control element is in the second position; and
the first and third ports in fluid communication with one another via the throat along a first flow path when the control element is in the first position.
2. The device of claim 1, wherein the first, second, and third ports are disposed perpendicular to an axis along which the control element moves between the first and second positions.
3. The device of claim 1, wherein at least portions of the first and second flow paths are disposed perpendicular to an axis along which the control element moves between the first and second positions.
4. The device of claim 1 , wherein the first valve seat is disposed between the first and second ports, and the second valve seat is disposed between the first and third ports.
5. The device of claim 1, wherein the first seating surface comprises a first tapered portion of the control element and the second seating surface comprises a second tapered portion of the control element.
6. The device of claim 5, wherein control element comprises a first reduced diameter portion and a second reduced diameter portion, and wherein the first tapered portion transitions to the first reduced diameter portion and the second tapered portion transitions to the second reduced diameter portion.
7. The device of claim 1, wherein the control element comprises a first reduced diameter portion and a second reduced diameter portion, and wherein the first reduced diameter portion forms part of the first flow path when the control element is in the second position, and wherein the second reduced diameter portion forms part of the second flow path when the control element is in the first position.
8. The device of claim 7, wherein the first reduced diameter portion is disposed adjacent a first tapered seating surface and the second reduced diameter portion is disposed adjacent a second tapered seating surface, and wherein the control element includes a widened portion between the first and second reduced diameter portions, and wherein the throat is sized larger than the widened portion to form a clearance space.
9. The device of claim 1, wherein the valve body includes a base sized to receive an upper valve insert secured by an upper valve cap, and a lower valve insert secured by a lower valve cap, the first flow path including an upper chamber formed between an upper portion of the base and the upper valve insert, the second flow path including a lower chamber formed between a lower portion of the base and the lower valve cap.
10. The device of claim 9, further comprising a control aperture formed in the upper valve cap and arranged for communication with an air supply source, and including a control piston disposed in a piston cavity formed in the upper valve cap, the control piston operatively coupled to the control element and arranged to shift the control element between the first and second positions in response to pressure changes in the piston cavity.
1 1. A high pressure fluid control device, comprising:
a valve body defining a first port, a second port, and a third port;
a throat formed within the valve body;
first and second valve seats mounted in the throat of the valve body, the first valve seat disposed between the first and second ports, the second valve seat disposed between the first and third ports; and
a control element disposed within the throat of the valve body and comprising a first seating surface and a second seating surface, the control element movable between a first position in which the first seating surface is seated against the first valve seat and a second position in which the second seating surface is seated against the second valve seat,
wherein the control element and the throat are arranged to permit selective fluid communication between the first and third ports along a first flow path when the control element is in the first position, and further to permit selective fluid communication between the first and second ports a second flow path when the control element is in the second position.
12. The device of claim 11, wherein the first, second, and third ports are disposed perpendicular to an axis along which the control element moves between the first and second positions.
13. The device of claim 11 , wherein at least portions of the first and second flow paths are disposed perpendicular to an axis along which the control element moves between the first and second positions.
14. The device of claim 1, wherein the first seating surface comprises a first tapered portion of the control element and the second seating surface comprises a second tapered portion of the control element.
15. The device of claim 14, wherein control element comprises a first reduced diameter portion and a second reduced diameter portion, and wherein the first tapered portion transitions to the first reduced diameter portion and the second tapered portion transitions to the second reduced diameter portion.
16. The device of claim 11, wherein the control element comprises a first reduced diameter portion and a second reduced diameter portion, and wherein the first reduced diameter portion forms part of the first flow path when the control element is in the second position, and wherein the second reduced diameter portion forms part of the second flow path when the control element is in the first position.
17. The device of claim 16, wherein the first reduced diameter portion is disposed adjacent a first tapered seating surface and the second reduced diameter portion is disposed adjacent a second tapered seating surface, and wherein the control element includes a widened portion between the first and second reduced diameter portions, and wherein the throat is sized larger than the widened portion to form a clearance space.
18. The device of claim 11, wherein the valve body includes a base sized to receive an upper valve insert secured by an upper valve cap, and a lower valve insert secured by a lower valve cap, the first flow path including an upper chamber formed between an upper portion of the base and the upper valve insert, the second flow path including a lower chamber formed between a lower portion of the base and the lower valve cap.
19. The device of claim 18, further comprising a control aperture formed in the upper valve cap and arranged for communication with an air supply source, and including a control piston disposed in a piston cavity formed in the upper valve cap, the control piston operatively coupled to the control element and arranged to shift the control element between the first and second positions in response to pressure changes in the piston cavity.
20. A high pressure fluid control device, comprising:
a valve body defining a first port, a second port, and a third port;
a throat disposed within the valve body and in fluid communication with each of the first, second, and third ports;
first and second valve seats mounted in the throat of the valve body;
a control element disposed within the throat of the valve body and comprising an axis disposed perpendicular to the first, second, and third ports, the control element movable along the axis between a first position in engagement with the first valve seat and a second position in engagement with the second valve seat;
the first and third ports in fluid communication with one another via the throat along a first flow path when the control element is in the first position; and
the first and second ports in fluid communication with one another via the throat along a second flow path when the control element is in the second position.
20. The device of claim 19, wherein at least portions of the first and second flow paths are disposed perpendicular to the axis of the control element.
21. The device of claim 19, wherein the first valve seat is disposed between the first and second ports, and the second valve seat is disposed between the first and third ports.
22. The device of claim 19, wherein the first seating surface comprises a first tapered portion of the control element and the second seating surface comprises a second tapered portion of the control element.
23. The device of claim 22, wherein control element comprises a first reduced diameter portion and a second reduced diameter portion, and wherein the first tapered portion transitions to the first reduced diameter portion and the second tapered portion transitions to the second reduced diameter portion.
24. The device of claim 19, wherein the control element comprises a first reduced diameter portion and a second reduced diameter portion, and wherein the first reduced diameter portion forms part of the first flow path when the control element is in the second position, and wherein the second reduced diameter portion forms part of the second flow path when the control element is in the first position.
25. The device of claim 24, wherein the first reduced diameter portion is disposed adjacent a first tapered seating surface and the second reduced diameter portion is disposed adjacent a second tapered seating surface, and wherein the control element includes a widened portion between the first and second reduced diameter portions, and wherein the throat is sized larger than the widened portion to form a clearance space.
26. The device of claim 19, wherein the valve body includes a base sized to receive an upper valve insert secured by an upper valve cap, and a lower valve insert secured by a lower valve cap, the first flow path including an upper chamber formed between an upper portion of the base and the upper valve insert, the second flow path including a lower chamber formed between a lower portion of the base and the lower valve cap.
27. The device of claim 26, further comprising a control aperture formed in the upper valve cap and arranged for communication with an air supply source, and including a control piston disposed in a piston cavity formed in the upper valve cap, the control piston operatively coupled to the control element and arranged to shift the control element between the first and second positions in response to pressure changes in the piston cavity.
PCT/US2008/066972 2007-06-15 2008-06-13 3-way high-pressure air operated valve WO2008157392A1 (en)

Priority Applications (11)

Application Number Priority Date Filing Date Title
EP20080771065 EP2165097B1 (en) 2007-06-15 2008-06-13 3-way high-pressure air operated valve
JP2010512394A JP5580195B2 (en) 2007-06-15 2008-06-13 Three-way high-pressure air operation valve
BRPI0812709 BRPI0812709A2 (en) 2007-06-15 2008-06-13 HIGH PRESSURE FLUID CONTROL DEVICE
CA2690099A CA2690099C (en) 2007-06-15 2008-06-13 3-way high-pressure air operated valve
MX2009013780A MX2009013780A (en) 2007-06-15 2008-06-13 3-way high-pressure air operated valve.
CN2008800197826A CN101743420B (en) 2007-06-15 2008-06-13 Three-way high-pressure pneumatic valve
AT08771065T ATE529674T1 (en) 2007-06-15 2008-06-13 HIGH PRESSURE AIR OPERATED 3-WAY VALVE
RU2009147675/06A RU2516049C2 (en) 2007-06-15 2008-06-13 Three-way valve with pneumatic actuator
KR1020107000845A KR101496350B1 (en) 2007-06-15 2008-06-13 High pressure fluid control device
AU2008265997A AU2008265997B2 (en) 2007-06-15 2008-06-13 3-way high-pressure air operated valve
NO20093430A NO339246B1 (en) 2007-06-15 2009-11-27 Three-way high-pressure, air-operated valve

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US94440707P 2007-06-15 2007-06-15
US60/944,407 2007-06-15
US12/137,905 US8991427B2 (en) 2007-06-15 2008-06-12 3-way high-pressure air operated valve
US12/137,905 2008-06-12

Publications (1)

Publication Number Publication Date
WO2008157392A1 true WO2008157392A1 (en) 2008-12-24

Family

ID=40131211

Family Applications (2)

Application Number Title Priority Date Filing Date
PCT/US2008/065084 WO2009005916A2 (en) 2007-06-15 2008-05-29 3-way high-pressure air operated valve
PCT/US2008/066972 WO2008157392A1 (en) 2007-06-15 2008-06-13 3-way high-pressure air operated valve

Family Applications Before (1)

Application Number Title Priority Date Filing Date
PCT/US2008/065084 WO2009005916A2 (en) 2007-06-15 2008-05-29 3-way high-pressure air operated valve

Country Status (13)

Country Link
US (1) US8991427B2 (en)
EP (1) EP2165097B1 (en)
JP (1) JP5580195B2 (en)
KR (1) KR101496350B1 (en)
CN (1) CN101743420B (en)
AT (1) ATE529674T1 (en)
AU (1) AU2008265997B2 (en)
BR (1) BRPI0812709A2 (en)
CA (1) CA2690099C (en)
MX (1) MX2009013780A (en)
NO (1) NO339246B1 (en)
RU (1) RU2516049C2 (en)
WO (2) WO2009005916A2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102853112A (en) * 2012-10-09 2013-01-02 瑞立集团瑞安汽车零部件有限公司 Pressure regulation type two-station three-way pneumatic control valve

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9010361B2 (en) * 2011-10-27 2015-04-21 Pentair Residential Filtration, Llc Control valve assembly
US9151401B2 (en) * 2011-12-29 2015-10-06 Tescom Corporation Fail-safe apparatus for use with fluid valves
US9217372B2 (en) * 2012-01-25 2015-12-22 Hamilton Sundstrand Corporation Fluid flow control device and method
US10508745B2 (en) * 2015-09-18 2019-12-17 The Oilgear Company Valve assembly
KR101616076B1 (en) * 2015-10-26 2016-04-27 (주)에이치에스 Anti Lock Break controlling device
CN108474488B (en) * 2016-01-14 2020-09-01 多可姆有限公司 Check valve with reverse fluid supply function
DE102016102388A1 (en) * 2016-02-11 2017-08-17 Hoerbiger Automatisierungstechnik Holding Gmbh proportional valve
DE102017222453A1 (en) * 2017-12-12 2019-06-13 Festo Ag & Co. Kg Valve
US11333254B2 (en) 2018-12-07 2022-05-17 Tescom Corporation Control valves
CN114729710B (en) * 2019-12-19 2023-12-05 美国圣戈班性能塑料公司 Lifting member, assembly and method of assembling and using same

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3858607A (en) * 1973-06-01 1975-01-07 Armco Steel Corp Three-way, two-position diverter valve
US4726398A (en) * 1986-12-16 1988-02-23 Marathon Oil Company High speed, high temperature three-way valve for switching high pressure fluids under low pressure control
US6105615A (en) * 1998-12-21 2000-08-22 Control Rain Systems, Inc. Control valve

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1076662A (en) * 1964-02-12 1967-07-19 Erich Herion A solenoid-operated multiway valve
US3461911A (en) * 1966-02-15 1969-08-19 Marotta Valve Co Magnetic latch for magnetically operated valve
US3762443A (en) * 1967-09-19 1973-10-02 Tektro Inc Resilient fluid control valve
JPS5874676U (en) * 1981-11-16 1983-05-20 エスエムシ−株式会社 solenoid valve
JPS5917074A (en) * 1982-07-16 1984-01-28 Hitachi Constr Mach Co Ltd Logic valve
US4694848A (en) * 1985-10-24 1987-09-22 Jorgensen Walter E Flow control valve
US4693267A (en) * 1986-03-31 1987-09-15 Tescom Corporation Self-venting pressure reducing regulator
RU2011090C1 (en) * 1989-11-21 1994-04-15 Белорусская государственная политехническая академия Three-way adjusting valve
US5345857A (en) * 1993-02-02 1994-09-13 Osmonics, Inc. Thermoplastic bellows and method of forming the same
CN2219979Y (en) * 1994-09-29 1996-02-14 水利部能源部地质勘探机电研究所 Direct-acting electromagnetic air valve
US5575311A (en) * 1995-01-13 1996-11-19 Furon Company Three-way poppet valve apparatus
DE10014133A1 (en) * 1999-03-23 2000-11-09 Fluoroware Inc Three-way valve
WO2001004718A1 (en) * 1999-07-09 2001-01-18 Tescom Corporation Electronic controlled pressure regulator system
JP2002250453A (en) * 2001-02-20 2002-09-06 Smc Corp Poppet type spool
US6772791B2 (en) * 2002-05-17 2004-08-10 Mac Valves, Inc. Directly operated pneumatic valve having an air assist return
US6691980B2 (en) * 2002-07-05 2004-02-17 Tescom Corporation Balanced valve with actuator
US20040007269A1 (en) * 2002-07-12 2004-01-15 Larsen Todd W. Inline pressure reducing regulator
US6820641B2 (en) * 2002-10-04 2004-11-23 Tescom Corporation Internally piloted dome loaded regulator
JP2006046414A (en) * 2004-08-02 2006-02-16 Smc Corp Three-port solenoid valve
US7210501B2 (en) * 2004-09-29 2007-05-01 Mac Valves, Inc. Directly operated pneumatic valve having a differential assist return

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3858607A (en) * 1973-06-01 1975-01-07 Armco Steel Corp Three-way, two-position diverter valve
US4726398A (en) * 1986-12-16 1988-02-23 Marathon Oil Company High speed, high temperature three-way valve for switching high pressure fluids under low pressure control
US6105615A (en) * 1998-12-21 2000-08-22 Control Rain Systems, Inc. Control valve

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102853112A (en) * 2012-10-09 2013-01-02 瑞立集团瑞安汽车零部件有限公司 Pressure regulation type two-station three-way pneumatic control valve
CN102853112B (en) * 2012-10-09 2014-09-03 瑞立集团瑞安汽车零部件有限公司 Pressure regulation type two-station three-way pneumatic control valve

Also Published As

Publication number Publication date
CA2690099A1 (en) 2008-12-24
WO2009005916A2 (en) 2009-01-08
RU2009147675A (en) 2011-07-20
BRPI0812709A2 (en) 2014-12-23
AU2008265997A1 (en) 2008-12-24
CA2690099C (en) 2016-02-23
KR20100049013A (en) 2010-05-11
NO20093430L (en) 2010-03-12
RU2516049C2 (en) 2014-05-20
US8991427B2 (en) 2015-03-31
CN101743420A (en) 2010-06-16
CN101743420B (en) 2012-05-30
KR101496350B1 (en) 2015-02-26
AU2008265997B2 (en) 2014-08-21
EP2165097A1 (en) 2010-03-24
NO339246B1 (en) 2016-11-21
WO2009005916A3 (en) 2009-12-30
JP2010530050A (en) 2010-09-02
US20080308163A1 (en) 2008-12-18
EP2165097B1 (en) 2011-10-19
JP5580195B2 (en) 2014-08-27
ATE529674T1 (en) 2011-11-15
MX2009013780A (en) 2010-04-22

Similar Documents

Publication Publication Date Title
CA2690099C (en) 3-way high-pressure air operated valve
US11079036B2 (en) Double action direction fluid flow valve
EP2236876B1 (en) Piloted poppet valve
US7658366B2 (en) High-pressure bi-directional valve
JP2014526025A (en) Fluid valve having a plurality of fluid flow control members
US20130037148A1 (en) Fluid valves having multiple fluid flow control members
EP1486712B1 (en) Three-way valve

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 200880019782.6

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 08771065

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2008265997

Country of ref document: AU

WWE Wipo information: entry into national phase

Ref document number: 2690099

Country of ref document: CA

WWE Wipo information: entry into national phase

Ref document number: 2010512394

Country of ref document: JP

Ref document number: MX/A/2009/013780

Country of ref document: MX

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2008265997

Country of ref document: AU

Date of ref document: 20080613

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 2008771065

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 95/CHENP/2010

Country of ref document: IN

ENP Entry into the national phase

Ref document number: 20107000845

Country of ref document: KR

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 2009147675

Country of ref document: RU

ENP Entry into the national phase

Ref document number: PI0812709

Country of ref document: BR

Kind code of ref document: A2

Effective date: 20091211