IPC분류정보
국가/구분 |
United States(US) Patent
등록
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국제특허분류(IPC7판) |
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출원번호 |
US-0377187
(1982-05-11)
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발명자
/ 주소 |
- Press, Irving D.
- Nickerson, Harvey R.
- Rink, Helm A.
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출원인 / 주소 |
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대리인 / 주소 |
Hopgood, Calimafde, Kalil, Blaustein & Judlowe
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인용정보 |
피인용 횟수 :
9 인용 특허 :
3 |
초록
▼
Connection between flange faces is effected with a rigid metal load bearing ring interposed therebetween for assuming the bolt torquing load and, when desired, for providing a fluid seal. Within said load bearing ring are disposed at least one coned ring spring and a force distributing ring for deve
Connection between flange faces is effected with a rigid metal load bearing ring interposed therebetween for assuming the bolt torquing load and, when desired, for providing a fluid seal. Within said load bearing ring are disposed at least one coned ring spring and a force distributing ring for developing a predetermined sealing force against a flare of non-metallic material, usually a plastic. The flare may be at the end of a pipe or fitting liner or associated with an auxiliary or adapter seal. The spring provides automatic compensation for any cold or hot flow of the material within the flare so as to maintain a fluid seal between said flare and a mating surface.
대표청구항
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1. An arrangement for establishing a fluid-tight seal between the faces of an assembled piping system flange connection, said arrangement comprising a rigid metal load bearing ring sized to fit between said flange faces with an inside diameter larger than the diameter of the fluid passage through sa
1. An arrangement for establishing a fluid-tight seal between the faces of an assembled piping system flange connection, said arrangement comprising a rigid metal load bearing ring sized to fit between said flange faces with an inside diameter larger than the diameter of the fluid passage through said piping system at said connection and with a predetermined axial length for engaging said flange faces upon assembly of said flange connection for establishing a cavity of predetermined size bounded by said flange faces, said inside diameter and said diameter of said fluid passage; and an assemblage of components comprising at least one subset consisting of a coned ring spring, a force distributing ring, and a radial flare from a tubular element of non-metallic material, said force distributing ring being located between and adjacent said radial flare and said coned ring spring, said assemblage being disposed within said load bearing ring for location within said cavity upon its establishment, the dimension in the axial direction and the configuration of said components of said assemblage being related to the axial direction dimensions of said load bearing ring such that when said assemblage and said load bearing ring are installed in said cavity in said flange connection along with a predetermined number, including zero, of other radial flares from tubular elements of non-metallic material associated with said flange connection, and with the radial flare of said subset in contact with a respective mating surface, in said subset said coned ring spring will be partially compressed for exerting a predetermined force through said adjacent force distributing ring against said adjacent radial flare to urge said adjacent radial flare into fluid sealing engagement with said mating surface. 2. An arrangement according to claim 1, wherein at least one of said flange faces is at the end of a flanged metal pipe, and of the elements of said one subset said radial flare of non-metallic material is at an end of a layer of said material lining said pipe and projecting therefrom with said one subset coned ring spring and said one subset force distributing ring mounted on said projecting lining layer between said one subset flare and said one flange face. 3. An arrangement according to claim 2, wherein another of said flange faces is at the end of a second flanged metal pipe, said second pipe also being lined with a layer of non-metallic material terminating in a second radial flare overlying a portion of said another flange face, and said mating surface is on said second radial flare. 4. An arrangement according to claim 1, wherein said load bearing ring comprises seal forming circular ribs projecting axially from opposite radial surfaces of said load bearing ring for engaging said flange faces in a fluid-tight seal. 5. An arrangement according to claim 1, wherein the convex side of said one subset coned ring spring faces said one subset force distributing ring. 6. An arrangement according to claim 5, wherein the inside diameter of said coned ring spring is substantially equal to the inside diameter of said force distributing ring such that said spring engages said force distributing ring close to the inside diameter of the latter. 7. An arrangement according to claim 6, wherein said force distributing ring is sufficiently rigid so as to avoid high localized loading in favor of broad surface distributed loading of said radial flare of said one subset under said force exerted by said one subset coned ring spring. 8. An arrangement according to claim 1, wherein said load bearing ring comprises seal forming means on opposite radial surfaces of said load bearing ring for engaging said flange faces in a fluid-tight seal. 9. An arrangement according to claim 2, wherein said load bearing ring comprises seal forming circular ribs projecting axially from opposite radial surfaces of said load bearing ring for engaging said flange faces in a fluid-tight seal. 10. An arrangement according to claim 2, wherein the convex side of said one subset coned ring spring faces said one subset force distributing ring. 11. An arrangement according to claim 10, wherein the inside diameter of said one subset coned ring spring is substantially equal to the inside diameter of said one subset force distributing ring such that said one subset coned ring spring engages said one subset force distributing ring close to the inside diameter of the latter. 12. An arrangement according to claim 11, wherein said one subset force distributing ring is sufficiently rigid so as to avoid high localized loading in favor of broad surface distributed loading of said radial flare of said one subset under said force exerted by said one subset coned ring spring. 13. An arrangement according to claim 1, wherein there is only one of said subsets and none of said other radial flares, and the total axial length, L, of said load bearing ring satisfies the equation, L=A+B+C+xD, to a close approximation, where x is a fraction, A, B and C are the thicknesses, respectively, of said radial flare, said force distributing ring, and said coned ring spring, and D is the height of the coned ring spring concavity. 14. An arrangement according to claim 1, wherein in addition to said one subset there is only one of said other radial flares, and the total axial length, L, of said metal load bearing ring satisfies the equation, L=2A+B+C+xD, to a close approximation, where x is a fraction, A, B and C are the thicknesses, respectively, of said radial flares, said force distributing ring, and said coned ring spring, and D is the height of the coned ring spring concavity. 15. An arrangement according to claim 1, wherein there are two of said subsets and none of said other radial flares, and the total axial length, L, of said metal load bearing ring satisfies the equation, L=2(A+B+C+xD), to a close approximation, where x is a fraction, A, B and C are the thicknesses, respectively, of said radial flares, said force distributing rings, and said coned ring springs, and D is the height of the coned ring spring concavity. 16. An arrangement according to claim 1, wherein there are two of said subsets and only one of said other radial flares, and the total axial length, L, of said metal load bearing ring satisfies the equation, L=3A+2(B+C+xD), to a close approximation, where x is a fraction, A, B and C are the thicknesses, respectively, of said radial flares, said force distributing rings, and said coned ring springs, and D is the height of the coned ring spring concavity. 17. An arrangement according to claim 1, wherein there are two of said subsets and two of said other radial flares, and the total axial length, L, of said metal load bearing ring satisfies the equation, L=4A+2(B+C+xD), to a close approximation, where x is a fraction, A, B and C are the thicknesses, respectively, of said radial flares, said force distributing rings, and said coned ring springs, and D is the height of the coned ring spring concavity. 18. An arrangement according to claim 1, wherein the concave side of said one subset coned ring spring faces said one subset force distributing ring. 19. An arrangement according to claim 18, wherein the outside diameter of said one subset coned ring spring is almost as large as the outside diameter of said one subset force distributing ring such that said one subset coned ring spring engages said one subset force distributing ring close to the outside diameter of the latter. 20. An arrangement according to claim 19, wherein the rigidity of said one subset force distributing ring is predetermined so as to avoid high localized loading in favor of broad surface distributed loading of said one subset radial flare under said force exerted by said one subset coned ring spring. 21. An arrangement according to claim 20, wherein said predetermined rigidity of the one subset force distributing ring is related to the force exerted thereon by said one subset coned ring spring within said cavity and to the radial taper in said one subset radial flare of non-metallic material so as to cup an amount substantially equal to said taper for establishing broad surface contact with the latter. 22. An arrangement according to claim 6, wherein said load bearing ring comprises at least one seal forming circular rib projecting axially from each of the opposite radial surfaces of said load bearing ring for engaging said flange faces in a fluid-tight seal. 23. An arrangement according to claim 19, wherein said load bearing ring comprises at least one seal forming circular rib projecting axially from each of the opposite radial surfaces of said load bearing ring for engaging said flange faces in a fluid-tight seal. 24. An arrangement according to claim 27, wherein said assemblage consists of an axial spacer ring in addition to two of said subsets, with said spacer ring being located between said coned ring springs for engagement therewith, there is none other radial flare, and the total axial length, L, of said metal load bearing ring satisfies the equation, L=2(A+B+C+xD)+E, to a close approximation where x is a fraction, A, B and C are the thicknesses, respectively, of said subset radial flares, said force distributing rings, and said coned ring springs, D is the height of the coned ring spring concavity, and E is the length of said axial spacer ring. 25. An arrangement according to claim 1, wherein said assemblage consists of an axial spacer ring in addition to two of said subsets with said spacer ring being located between said coned ring springs for engagement therewith, there is one of said other radial flares, and the total axial length, L, of said metal load bearing ring satisfies the equation, L=3A+2(B+C+xD)+E, to a close approximation, where x is a fraction, A, B and C are the thicknesses, respectively, of said radial flares, said force distributing rings, and said coned ring springs, D is the height of the coned ring spring concavity, and E is the length of said axial spacer ring. 26. An arrangement according to claim 1, wherein said assemblage consists of an axial spacer ring in addition to two of said subsets with said spacer ring being located between said coned ring springs for engagement therewith, there are two of said other radial flares, and the total axial length, L, of said metal load bearing ring satisfies the equation, L=4A+2(B+C+xD)+E, to a close approximation, where x is a fraction, A, B and C are the thicknesses, respectively, of said radial flares, said force distributing rings, and said coned ring spring, D is the height of the coned ring spring concavity, and E is the length of said axial spacer ring.
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