CROSS REFERENCE TO RELATED APPLICATION

This application claims priority to U.S. Application No. 62/155,494 filed on May 1 , 2015, the disclosure of which is incorporated herein by reference for all purposes.

FIELD OF THE INVENTION

The present invention relates to couplings for pipe. In particular, the present invention relates to a coupling connection having primary and secondary sealing mechanisms.

BACKGROUND OF THE INVENTION

Typical prior art bolted pipe coupling systems comprise a pair of flanged hubs having hub faces, a compression assembly for urging the hub faces together, and a sealing member disposed between the hub faces. When the compression assembly urges the hubs together, it forms a seal.

Such prior art couplings are limited in the materials with which they can be used. Because the gasket is oftentimes exposed to the materials flowing through the coupled pipes, care must be used to select the material of the gasket so as to not be dissolved, corroded, or otherwise destroyed by the flowing media. In many prior art couplings, the gasket serves as the only seal between abutted faces of the hubs. SUMMARY OF THE INVENTION

In one aspect, the present invention provides a pipe coupling for joining two tubular members, namely pipe. The pipe coupling has two metal-to-metal seals to prevent leakage. The engagement of the hub faces of the coupling of the present invention forms a primary metal-to-metal seal. A seal ring within a seal ring groove in the hub faces forms a secondary metal-to-metal seal. The seal ring is isolated from the fluid media flowing through the pipes unless the primary seal fails. This increases the lifespan of the coupling significantly.

These and further features and advantages of the present invention will become apparent from the following detailed description, wherein reference is made to the figures in the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

Fig. 1 is an isometric view of the coupling assembly of the present invention.

Fig. 2 is a side elevational view of the coupling assembly shown in Fig. 1. Fig. 3 is a cross-sectional view taken along the lines A— A in Fig. 2.

Fig. 4A is a side elevational view of the hub of the present invention.

Fig. 4B is a cross-sectional view taken along the lines C— C shown in Fig.

4A.

Fig. 5A is a top view of the clamp of the present invention.

Fig. 5B is a bottom view of the clamp of the present invention.

Fig. 6 is an elevational view of the clamp of the present invention.

Fig. 7 is a cross-sectional view taken along the lines B— B of Fig. 6.

Fig. 8A is an elevational view of a partial assembly of the coupling of the present invention.

Fig. 8B is a cross-sectional view taken along the lines B— B of Fig. 8A.

Fig. 9A is an elevational view of a partial assembly of the coupling of the present invention.

Fig. 9B is a cross-sectional view taken along the lines B— B of Fig. 9A.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS

The present invention is not limited to use with specific tubulars and can be used with steel pipe, polymeric pipe, polymer-lined pipe, hose, or other conduits which transport gas, fluid, semi-fluid, or solid matter.

As used herein, the terms "axially outermost," "axially outwardly facing,"

"axially innermost," "axially inwardly facing," and the like refer to the respective axially outer and inner portions of the pipe coupling assembly itself. It will be appreciated that one or more couplings may be employed in a string of pipes. The description of the axially outermost and innermost components of the coupling does not mean they are outermost or innermost pieces on a string of pipe.

Turning to Figs. 1-3 there is shown, generally as 10, the coupling assembly of the present invention. The coupling assembly 10 is made up of two annular hubs 20a and 20b and clamp assembly 50 comprised of clamp members 50a and 50b. Each of hubs 20a and 20b has flow passageways 21a and 21 b, respectively therethrough. Clamp members 50a and 50b each have a plurality of bolt holes 14. When the clamp members 50a and 50b are positioned on hubs 20a and 20b, bolt holes 14 on respective clamp members are in register. Bolts 15 pass through registering bolt holes 14, and nuts 18 are threaded onto the outer ends of bolts 15 to compress clamp members 50a and 50b together. If needed washers 19 or the like can be positioned between the nuts 18 and the clamp members 50a and 50b. As seen in Fig. 3, each of hubs 20a and 20b have seal grooves 30a and 30b, respectively, in which seal ring 40 is fitted. As will be discussed more hereafter, seal ring 40 forms a secondary metal-to-metal seal.

Turning to Fig. 4A there is shown hub 20a. Fig. 4B shows a portion of hub 20a in cross-section. It will be understood that hub 20b is a mirror image of 20a and thus has the same components and will not be described separately. Those parts present on both hubs will be given the same reference numbers and differentiated by the letters "a" and "b", e.g., seal grooves 30a and 30b are found on respective hubs 20a and 20b.

Hub 20a includes first axial end 22a and second axial end 23a. First axial end 22a is the axially outermost end to which a pipe end is connected by welding or other appropriate means. Second axial end 23a is the axially innermost end of hub 20a and includes radially outwardly extending annular flange portion 25a. The flange portion 25a of hub 20a has an annularly extending, axially outwardly facing frustoconical flange surface 26a. Second axial end 23a also has axially inwardly facing, frustoconical or tapered seal face 27a. The radially innermost portion of seal face 27a, directly and surroundingly adjacent passageway 21a, forms an annular seat 28a which is perpendicular to the direction of passageway 21a. Perpendicular seat 28a can be only several thousandths of an inch long. As shown in Fig. 4, the seal face 27a radially outwardly from seat 28a is tapered at angle X. The importance of the tapered seal face 27a and seat 28a will be explained hereafter.

Formed in seal face 27a is an annular seal ring groove 30a, seal ring groove 30a being shaped to receive a portion of seal ring 40. In a preferred embodiment, the radially outer surface of seal ring grooves 30a and 30b are tapered relative to the direction of passageways 21a and 21b, preferably at an angle of from about 13.0° to about 17.0°, most preferably 15.0°. As best seen in Fig. 3, seal grooves 30a and 30b of hub 20a and 20b are in register with one another and form a seal ring channel 45. Seal ring 40 is disposed in seal ring channel 45. Seal ring 40 tapers such that the thickest point is generally in the center and the axially extending sides are tapered. The angle of taper of the axially extending, radially outer surfaces of seal ring 40 is preferably from about 13.0° to about 18.0°, most preferably about 17.0°. It will be appreciated that the angles of taper of the seal ring groove and the seal ring will vary depending on the materials used.

Turning to Figs. 5-7, there is shown clamp member 50a of the present invention. It will be understood that clamp member 50b is the same shape and has the same features as clamp member 50a and will thus not be described separately. Clamp member 50a is comprised of generally arcuate central body portion 52a and wings 54a which extend laterally outwardly from opposite sides of body 52a. Each wing 54a has at least one bolt hole 14a extending therethrough. In a preferred embodiment, each wing 54a has a plurality of bolt holes. It will be understood that the exact number of bolt holes can vary and the invention is not limited to a specific number of bolt holes 14a. Body 52a of clamp member 50a has an outer surface 55a and an inner surface 56a. As can best be seen with reference to Fig. 7, inner surface 56a has a groove 57a profiled to overlap the flange portions 25a and 25b of hubs 20a and 20b. In particular, groove 57a has two axially inwardly facing frustoconical surfaces 58a complementary to the axially outwardly facing frustoconical surfaces 26a and 26b of hubs 20a and 20b. In a preferred embodiment, the angle of taper of surfaces 26a and 26b is from 22.0° to about 27.0°, most preferably 25.0°, from a plane running perpendicular to pathways 21a and 21 b. The exact angle of taper can vary depending on the materials of which the hub is made.

Turning to Figs. 8 and 9 there is shown the operation of the coupling assembly of the present invention. It will be appreciated that axially outer ends 22a and 22b of hubs 20a and 20b would be welded or otherwise attached to the pipes or other tubular members to be coupled together. The attachment of pipes to coupling hubs is well known to those skilled in the art. As best seen in Fig. 8B, prior to clamp members 50a and 50b being tightened, the radially inner seats 28a and 28b of hubs 20a and 20b are engaged. The frustoconical seal faces 27a and 27b of hubs 20a and 20b are not yet engaged due to their taper. As best seen in Fig. 8B, faces 27a and 27b taper axially away from one another, leaving a gap between them when the connection is not fully made up. Turning to Fig. 9B, when clamp members 50a and 50b are engaged and initially tightened the inwardly facing surfaces 58a of the clamp member 50a engage the outwardly facing surfaces 26a and 26b of the hubs 20a and 20b. Similarly, the inwardly facing surface 58b of the clamp member 50b engage the outwardly facing surfaces 26a and 26b of the hubs 20 and 20b. The engagement by clamps 50a and 50b force seal faces 27a and 27b together. As clamp assembly 50 is further tightened, hubs 20a and 20b are forced against one another in the direction of arrows A. Thus, as seen in Fig. 9B, the gap between seal faces 27a and 27b at the radially outermost portion of the hubs closes.

The taper of the seal faces 27 is important to the operation of the coupling of the present invention. Forcing the tapered faces 27a and 27b together induces high contact stresses and yielding of the metal adjacent passageways 21a and 21b. It will be appreciated that the exact angle of taper of faces 27a and 27b varies based on the material of the hubs. In a preferred embodiment though the angle of taper is from 0.10° to about 0.30°, most preferably 0.10°, relative to a plane perpendicular to the direction of passageways 21a and 21b. The taper extends along substantially the entire faces 27a and 27b. Only seats 28a and 28b, which can be only a few thousandths of an inch are perpendicular to the direction of passageways 21a and 21b.

It will be apparent from Fig. 9 that when the coupling assembly is fully made up, the engagement of perpendicular seats 28a and 28b forms the primary metal-to-metal seal. Since there is no gap between the seats 28a and 28b, turbulence, erosion and crevice corrosion at the joint interface is virtually eliminated, allowing for a streamlined flow of the media through the coupling. Seal ring 40 in interference fit with the tapered surfaces of seal ring grooves 30a and 30b forms the secondary metal-to-metal seal. This provides a distinct advantage over the prior art coupling assemblies as the seal ring 40 is isolated from direct exposure to internal fluids as long as the primary seal is intact. If the primary seal is compromised, the seal ring 40 is pressure activated by the internal pressure of the fluid. It will be appreciated that the seal ring 40 also assists in guiding the joint during make-up.

Although specific embodiments of the invention have been described herein in some detail, this has been done solely for the purposes of explaining the various aspects of the invention, and is not intended to limit the scope of the invention as defined in the claims which follow. Those skilled in the art will understand that the embodiment shown and described is exemplary, and various other substitutions, alterations and modifications, including but not limited to those design alternatives specifically discussed herein, may be made in the practice of the invention without departing from its scope.