Shock absorbing sealing means for flow control devices

Abstract: A flow control device illustrated as a pressure relief valve (10, 10A) has a reciprocable valve member (22, 22A) for seating on a face (20, 20A) of a fixed seat ring (18, 18A). The valve member (22, 22A) includes a hub (36, 36A), an outer seal ring (38, 38A), and a flexible connecting member (40, 40A) extending between and connecting the seal ring (38, 38A) and the hub (36, 36A). Upon seating or reseating of valve member (22, 22A) seal ring (38, 38A) contacts fixed seat ring (18, 18A) and flexible connecting member (40, 40A) flexes upon relative movement of the hub (36, 36A) after initial contact of the seal ring (38, 38A) with the fixed seat ring (20, 20A) to act as a shock absorber for absorbing impact forces.

Description: This invention relates to fluid operated valves and to valve members therefor. Heretofore, such as shown in US-A-3,433,250, safety relief valves have been provided with means to absorb at least some of the impact forces upon reseating of a valve disk. However, upon reseating of the valve disk, substantial radial deflection may occur after initial line contact of the disk sealing face with the fixed seat ring. Such radial deflection is undesirable and oftentimes results in undue wear and possible damage to the contacting faces. Also, shock absorbing sealing means for flow control devices such as valves, have utilized elastomeric members for absorbing shock. For example, US-A-4,858,642 shows a pressure operated relief valve in which an elastomeric member is positioned between a valve disc and a disc holder to absorb shock forces upon seating of the valve member resulting from a reduction in pressure for actuation of the valve member. Elastomeric members are subject to deterioration at high temperatures, such as temperatures over around 260°C (500°F) for example. Other impact type valves have utilized fluid metering for absorbing shock force upon impact of the valve member against a valve seat or for reducing the speed of movement of the valve member prior to impact thereby to minimize impact forces. Such fluid metering arrangements are costly, relatively complex, and do not usually absorb all of the impact forces. US-A-4858642 discloses a fluid operated valve having a valve body including a flow passage and a hard annular seat ring mounted within the valve body about the flow passage, and a fluid pressure responsive reciprocable valve member mounted within the valve body for movement between opened and closed positions relative to the flow passage and adapted to seat in the closed position on the hard seat ring, the valve member including a central hub, an outer annular seal ring having radially inner and outer peripheral surfaces and a connecting member extending between the hub and the seal ring. The fluid operated valve in accordance with the present invention has the above-defined features of the valve of US-A-4858642 but is characterized in that the outer annular seal ring is a hard seal ring for seating in face-to-face contact relation with the seat ring in the closed position of the valve member, in that the radially inner and outer peripheral surfaces on the hard seal ring are spaced radially from the central hub, and in that the connecting member is flexible for flexing between the central hub and the inner peripheral surface of the seal ring after initial contact of the hard seal ring with the hard seat ring to absorb impact loads resulting from contact of the hard seal ring against the hard seat ring without substantial movement of the hard seal ring. Thus, the present invention is directed to a valve in which a reciprocable valve member seats against a hard seat with at least some of the impact forces being absorbed after contact of the valve member against the seat. To minimize wear, damage, leakage, and the like to the impacting members, that the impact forces or energy generated by the impact are dissipated or absorbed with minimal radial deflection between contacting faces. More particularly, the flexible connecting member between the valve hub and the annular seal ring permits by flexure thereof a cushioned longitudinal movement of the valve hub or body after contact of the seal ring with the seat ring to absorb impact forces. The connecting member is preferably inclined a predetermined amount from a true radial relation to control radial deflection of the seal ring. Bending moments are exerted at the joining, preferably hinging, of opposite ends of the flexible connecting member to the valve hub and to the hard seal ring. Thus, the size of the flexible connecting member and the seal ring may be predetermined depending on the specifications and operating parameters for the valve structure. The present invention also encompasses the improved valve member itself. Preferred embodiments of a valve and valve member in accordance with the present invention will now be described with reference to the accompanying drawings, in which: Figure 1 is a cross section of a pilot operated pressure relief valve with the improved valve member of this invention shown in a closed position; Figure 2 is a cross section of the pilot operated pressure relief valve shown in Figure 1 with the valve member shown in an open position to permit fluid flow through the valve for relieving fluid pressure; Figure 3 is an enlarged view of the reciprocable valve member of Figures 1 and 2 removed from the valve body; Figure 4 is an enlarged fragment of Figure 3 illustrating particularly the sizing of the members forming the shock absorbing sealing means of the present invention and showing in broken lines the final position of the valve member after flexing of the connecting member; Figure 5 is a cross section of another embodiment of the present invention showing a non-pilot operated pressure relief valve in closed position; Figure 6 is an enlarged fragment of Figure 5 showing the valve member utilized therein; and Figure 7 is an enlarged section of the valve member showing a portion thereof in seated position with the connecting member shown in broken lines in flexed position for absorbing impact forces after seating of the sealing means. DESCRIPTION OF THE INVENTION Referring now to the drawings and more particularly to the embodiment shown in Figures 1-4, a pilot operated safety relief valve is shown generally at 10 having a valve body 12 defining an inlet flow passage at 14 and an outlet flow passage at 16. A nozzle or seat ring is shown generally at 18 and has a generally planar seat face at 20. An improved reciprocable valve member is generally indicated at 22 having a dome chamber 24 therein and mounted for movement between open and closed positions. A metering or dampening chamber is shown at 26 (Fig. 2) to reduce the impact of valve member 22 against seat ring 18 when moving to closed position after being opened. A pilot valve for controlling relief valve 10 is shown schematically at 28 having an inlet line 30 in fluid communication with inlet 14 and a dome line 32 extending to dome chamber 24. An exhaust or discharge line 34 extends to atmosphere. Valve member 22 includes a body 35 having a disk including central hub shown generally at 36, an outer seal ring shown generally at 38, and a flexible connecting member shown generally at 40 extending between and connecting hub 36 to seal ring 38. Seal ring 38 has a planar sealing face 42 between radially inner and outer peripheral surfaces thereof adapted to contact and seat on face 20 of seat ring 18 upon closing of valve member 22 after opening thereof. Valve member 22 moves to an open position as shown in Figure 2 resulting from a predetermined high fluid pressure being reached in inlet passage 14 sensed by pilot line 30. Upon a reduction in fluid pressure in inlet fluid passage 14 as sensed by pilot valve 28, valve member 22 reseats on seat ring 18. Oftentimes, even with dampening of the movement of valve member 22, and particularly upon a relative fast reduction in fluid pressure in fluid inlet passage 14 after opening, valve member 22 moves rapidly to closed seated position to exert impact forces against seat ring 18. Impact forces may cause abnormal wear or damage which could effect fluid leakage in the closed position of valve member 22. The present invention utilizes a flexible connecting member 40 between hub 36 and the inner radial periphery of outer seal ring 38 which flexes after initial contact of seal ring 38 with seat ring 18 for absorbing impact forces. Flexible connecting member 40 is constructed and arranged for a predetermined flexure relative to seal ring 38 for absorbing impact forces with minimal radial and angular deflection of sealing face 42 on seal ring 38 and for providing alignment between faces 20 and 42. As shown in Figure 4, central hub 36 of valve member 22 moves an axial distance D after contact of seal face 42 with seat face 20. Distance D is at least greater than around 0.0508mm (0.002 inch) and may be as high as around 0.762mm (0.030 inch) or greater depending primarily on such factors as the size of valve member 22 and various operating parameters. Seat ring 38 has a planar rear face 41 and valve member body 35 has an opposed face 43 normally spaced from face 41 and acting as a stop upon contact with rear face 41 to limit the maximum travel S of hub 36 past the elastic limit of connecting member 40 after seat face 20 is contacted by seal ring 38. Hub 36 is secured to body 35 of valve member 22 by a threaded bolt shown at 44 threaded within an internally threaded opening 45 in hub 36. Longitudinal axis of flexible connecting member 40 is shown at 46 (Fig. 4). Connecting member 40 is hinged to hub 36 at point 48, and hinged to seal ring 38 at 50. The thickness of connecting member 40 is indicated at T. Seal ring 38 has a maximum thickness indicated at T1, and a width indicated at W. The center of gravity of seal ring 38 is indicated at 52 and is offset an axial distance D1 from the center line of connecting member 40 at hinge point 50 in a direction away from or longitudinally outwardly of seal face 42. Such an offset has been found desirable in order to minimize any angular or radial deflection of seal face 42 upon flexing of connecting member 40 resulting from movement of hub 36 after seal face 42 contacts seat face 20. An offset distance D1 of at least around 1.27mm (0.050 inch) is believed desirable in order to minimize the deflection of the seal face 42 to an insignificant amount. Further, in order for the flexing of connecting member 40 to maintain alignment of seal face 42 against seat face 20 upon impacting of seal ring 38 against seat ring 18, it is desirable that the maximum thickness T1 of seal ring 38 be at least around twice the thickness T of connecting member 40, and that the total width W of seal ring 35 be at least around three times the thickness T of connecting member 40. Additionally, in order to minimize the angular and radial deflection of face 42 upon flexure of connecting member 40, the longitudinal axis 46 of connecting member 40 is inclined rearwardly to provide a negative slope shown at angle A. It is believed that angle A should be between around one-half degree and ten degrees in order to obtain a satisfactory result. Planar face 42 is of a width greater than the width of planar face 20 for the most effective sealing action and with minimal radial and angular deflections occurring after contact. Such an arrangement accommodates any lack of concentricity between rings 18 and 38. It is noted that seal face 42 is wider than seat face 20 since seal face 42 is formed of a harder face material. It is apparent from the above that the design of the flexible connecting member 40 between seal ring 38 and hub 36 may be predetermined in order to have sufficient flexure to absorb the impact forces while minimizing the deflection of seal face 42. While hub 36, connecting member 40, and seal ring 35 are shown as an integral construction, it is to be understood that connecting member 4'0 may be formed of a separate member, if desired, such as a Belleville washer. While metals are the preferred materials from which the seat ring 18 and seal ring 38 are formed, it is to be understood that other hard materials resistant to high temperature, such as certain types of ceramic and composite materials, may be utilized in a satisfactory manner. The term "hard" as used in the specification and claims herein is interpreted as being "non-elastomeric". Referring now to Figure 5-7, another embodiment of the present invention is illustrated for a pressure relief valve which is not pilot operated. Pressure relief valve 10A has a valve body 12A including an inlet flow passage 14A and an outlet flow passage 16A. A nozzle or seat ring 18A has a planar seat face 20A. A spindle 22A has a bore 45A. Improved pressure relief valve 10A includes hub 36A fitted within bore 45A, a seal ring 38A, and a flexible connecting member 40A. A spring 57A urges spindle 22A and seal ring 38A into seated position on face 20A of seat ring 18A. Upon a predetermined high fluid pressure being reached in inlet fluid passage 14A, spindle 22A and seal ring 38A are forced outwardly against the bias of spring 57A to permit fluid flow through fluid passage 16A. Upon a reduction in fluid pressure in inlet 14A, spindle 22A under the bias of spring 57A moves seal ring 38A to reseated position on face 20A of seat ring 18A. Flexible connecting member or web 40A functions in the same manner as the embodiment of Figure 1-4 and is generally identical to the embodiment of Figure 1-4 except for the slope of connecting member 40A shown at angle A and the location of the center of gravity shown at point 52A. The longitudinal axis 46A of connecting member 40A has a positive slope shown at angle A between hinge points 48A and 50A. Angle A is generally equal to angle A in the embodiment of Figures 1-4 but slopes in a direction toward face 42A instead of away from face 42A as in the embodiment of Figures 1-4. Additionally, in order to minimize deflection of face 42A after contact against face 20A, the center of gravity 52A of seal member 38A is positioned forwardly of hinge point 50A toward face 42A as shown at D1. Distance D1 is generally identical to the distance D1 in the embodiment shown in Figures 1-4 except in an opposite direction thereby to minimize the deflection of face 42A resulting from the flexing of connecting member 40A. Hub 36A moves a distance D as in the embodiment of Figures 1-4 and faces 41A and 43A engage in abutting contact to limit the movement of hub 36A past the elastic limit of connecting member 40A. While the present invention has been illustrated for utilization with pressure relief valves, it is to be understood that this invention could be utilized with other types of valves such as check valves, where a reciprocable valve member is provided for seating and reseating against an annular seat ring.

Claims: A fluid operated valve (10, 10A) having a valve body (12, 12A) including a flow passage and a hard annular seat ring (18, 18A) mounted within the valve body about the flow passage, and a fluid pressure responsive reciprocable valve member (22, 22A) mounted within the valve body for movement between opened and closed positions relative to said flow passage and adapted to seat in the closed position on said hard seat ring, said valve member including a central hub (36, 36A), an outer annular seal ring (38, 38A) having radially inner and outer peripheral surfaces and a connecting member (40, 40A) extending between said hub and said seal ring, characterized by: said outer annular seal ring (38, 38A) being a hard seal ring for seating in face-to-face contact relation with said seat ring in the closed position of said valve member, and said radially inner and outer peripheral surfaces on said hard seal ring being spaced radially from said central hub; and said connecting member (40, 40A) being flexible for flexing between said central hub (36, 36A) and said inner peripheral surface of said seal ring after initial contact of said hard seal ring (38, 38A) with said hard seat ring (18, 18A) to absorb impact loads resulting from contact of said hard seal ring against said hard seat ring without substantial movement of said hard seal ring. A fluid operated valve as set forth in Claim 1, wherein said seal ring (38, 38A) and said hard seat ring (18, 18A) have generally planar sealing faces (42, 42A, 20, 20A) in contact with each other in the closed position of said valve member. A fluid operated valve as set forth in Claim 2, wherein said sealing faces (42, 42A) of said hard seal ring (38, 38A) are of a width greater than the width of said seal face (20, 20A) on said hard seat ring (18, 18A), said sealing faces initially contacting each other along substantially the entire width of said seat ring face (18, 18A) and providing minimal deflection between said contacting faces. A fluid operated valve as set forth in any preceding claim, wherein said connecting member (40, 40A) is hinged at opposed ends thereof to said central hub (36, 36A) and to said hard seal ring (38, 38A). A fluid operated valve as set forth in any preceding claim, wherein said connecting member (40, 40A) is slanted from said central hub (36, 36A) to said hard seat ring (18, 18A) a predetermined amount in a direction at right angles to a radial direction, thereby to provide increased resistance to radial deflection of said seal ring after initial contact of said seal ring against said hard seat ring. A fluid operated valve as set forth in Claim 5, wherein said connecting member (40) is slanted in a direction away from said hard seat ring (18) with the center of gravity (52) of said hard seal ring (38) being positioned axially outwardly of said connecting member relative to said hard seat ring for minimizing radial deflection of the seal ring. A fluid operated valve as set forth in Claim 5, wherein said connecting member (40A) is slanted in a direction toward said hard seat ring (18A) with the center of gravity (52A) of said hard seal ring (38A) being positioned axially inwardly of said connecting member relative to said hard seat ring for minimizing radial deflection of the seal ring. A fluid operated valve as set forth in Claim 6 or Claim 7 when appendant to Claim 4, wherein said center of gravity (52, 52A) is offset at least 1.27 mm (0.050 inch) in a direction parallel to the longitudinal axis of said connecting member (40, 40A) from a hinge point (50, 50A) of said connecting member to said hard seal ring (38, 38A). A fluid operated valve as set forth in any preceding claim, wherein after initial contact of said hard seal ring (38, 38A) with said hard seat ring (18, 18A), said central hub (36, 36A) moves longitudinally relative to said seal ring a distance sufficient to absorb impact loads resulting from contact of said hard seal ring against said hard seat ring. A fluid operated valve as set forth in Claim 9, wherein said central hub (36, 36A) moves relative to said seal ring a distance of at least 0.0508 mm (0.002 inch). A fluid operated valve as set forth in Claim 10, wherein said distance is from 0.0508 mm (0.002 to 0.030 inch). A fluid operated valve as set forth in any preceding claim, wherein said central hub (36, 36A) and said connecting member (40, 40A) are integral. A fluid operated valve as set forth in any preceding claim, wherein said seal ring (38, 38A) and said connecting member (40, 40A) are integral. A fluid operated valve as set forth in Claim 12 or Claim 13, wherein said central hub (36, 36A), said seal ring (38, 38A) and said flexible connecting member (40, 40A) are a one-piece integral structure. A fluid operated valve as set forth in any preceding claim, wherein said seal ring (38, 38A) has a width as measured in a direction parallel to the longitudinal axis (46, 46A) of said connecting member (40, 40A) at least three times the thickness of said connecting member. A fluid operated valve as set forth in any preceding claim, wherein said seal ring (38, 38A) has a thickness as measured in a direction transverse to the longitudinal axis (46, 46A) of said connecting member (40, 40A) at least twice the thickness of said connecting member. A fluid operated valve as set forth in any preceding claim, wherein said hard seat ring (18, 18A) is a metal seat ring fixed within the valve body (12, 12A). A valve member (22, 22A) for mounting within a flow passage of a fluid operated valve for reciprocal movement in response to fluid pressure between opened and closed positions relative to the flow passage and adapted to seat in the closed position on a hard annular seat ring mounted about the flow passage, the valve member including a central hub (36,36A), an outer annular seal ring (38,38A) having radially inner and outer peripheral surfaces and a connecting member (40,40A) extending between said hub and said seal ring, characterized by: said outer annular seal ring (38,38A) being a hard seal ring for seating in face-to-face contact relation with the seat ring of the valve in the closed position of the valve member and said radially inner and outer peripheral surfaces on said hard seal ring being spaced radially from said central hub; and said connecting member (40,40A) being flexible for flexing between said central hub (36,36A) and said inner peripheral surface of said seal ring whereby said hard seal ring (38,38A) is adapted to absorb impact loads following initial contact of said hard seal ring against the hard seat ring of the valve without substantial movement of said hard seal ring. A valve member as set forth in Claim 18, wherein said connecting member (40, 40A) is hinged at opposed ends thereof to said central hub (36, 36A) and to said hard seal ring (38, 38A). A valve member as set forth in Claim 18 or Claim 19, wherein said central hub (36, 36A) and said connecting member (40, 40A) are integral. A valve member as set forth in any one of Claims 18-20, wherein said seal ring (38, 38A) and said connecting member (40, 40A) are integral. A valve member as set forth in Claim 20 or Claim 21, wherein said central hub (36, 36A), said seal ring (38, 38A) and said flexible connecting member (40, 40A) are a one-piece integral structure. A valve member as set forth in any one of Claims 18-22, wherein said seal ring (38, 38A) has a width as measured in a direction parallel to the longitudinal axis (46, 46A) of said connecting member (40, 40A) at least three times the thickness of said connecting member. A valve member as set forth in any one of Claims 18-23, wherein said seal ring (38, 38A) has a thickness as measured in a direction transverse to the longitudinal axis (46, 46A) of said connecting member (40, 40A) at least twice the thickness of said connecting member. A valve member as set forth in any one of Claims 18-23, wherein said seal ring (38, 38A) has generally planar sealing faces (42, 42A) for contacting correspondingly planar sealing faces on the seat ring of the valve member. A valve member as set forth in any one of Claims 18-25, wherein said connecting member (40, 40A) in its unflexed position is slanted from said central hub (36, 36A) to said hard seal ring (38, 38A) a predetermined amount in a direction at right angles to a radial direction, thereby to provide increased resistance to radial deflection of said seal ring on contact with the seat ring of the valve member. A valve member as set forth in Claim 19, or in any one of Claims 20-26 when appendant to Claim 19, wherein the center of gravity (52, 52A) of said hard seal ring (38, 38A) is offset at least 1.27 mm (0.050 inch) in a direction parallel to the longitudinal direction of said connecting member (40, 40A) from a hinge point (50, 50A) of said connecting member to said hard seal ring (38, 38A).

Inventors: ALBERTS JACK B, MCNEELY MICHAEL D, ALBERTS, JACK B, MCNEELY, MICHAEL D
Applicants: KEYSTONE INT, KEYSTONE INTERNATIONAL HOLDINGS CORP.
Application year: 1991
Main classification: F16K47
IPC codes: F16K17, F16K47