The present invention relates to a mechanical seal assembly, in particular a mechanical seal assembly for providing a metal-to-metal seal within a flanged connection.

Flanges are widely used for connecting two pipes together, or when connecting a pipe to a valve, pump and other auxiliary device for controlling or monitoring flow within a flow line, for example.

A wholly conventional flange takes the form of a flange body having first and second ends and a fluid bore of circular cross section extending between the first and second ends. A first end of the fluid bore is exposed at the first end of the flange body, and the first end of the flange body is of larger diameter than the second end of the flange body, defining a flange connection face concentric with the fluid bore. A plurality of bolt holes are provided through the first end, off-set from the fluid bore and extending in a direction parallel with the central axis of the fluid bore.

When connecting two pipes together, a flanged joint can be made by bolting together two flanges, with a gasket clamped between them to provide a pressure seal. When connecting a pipe to a valve, pump and other auxiliary device (e.g. for controlling or monitoring flow within a flow line), the auxiliary device will typically a flanged connection face configured for bolted connection with the flange connection face of a conventional flange, with a gasket clamped between the flanged connection face of the auxiliary device and the flange connection face of the conventional flange.

Conventional flanges are approved for use under certain pressure and/or temperature conditions according to one or more widely recognised standards, such as the American National Standards Institute (ANSI). Depending on the material the flange is made from, such as cast iron or steel, and the type of connection required to attach the flange to a pipe (e.g. via a welded or threaded connection), standard class ratings are determined, such as to provide a pressure/temperature rating or required bolt and nut dimensions etc. In the oil and gas industry, for example, flanges are expected to withstand high pressures and the ANSI standards provide consumers with important information on the characteristics and performance of the flange, as well as an assurance that they are receiving the right product for their particular application.

The ANSI B16.5 pipe flanges are rated from Class 150 through to Class 2500 which allow for hydrostatic test pressures ranging from 400 psi (2.76 MPa) up to just under 10,000 psi (68.95 MPa).

As the operating pressure of a pipeline incorporating a flanged joint increases, more force is required to compress the gasket and contain the force acting on the seal. This requirement drives the size and complexity of the bolt configuration, thus necessitating a larger flange to accommodate the bolting requirements at higher pressures.

For example, a Standard 2 inch Class 150 flange will have an outside diameter of 6 inches (152.40 mm) and a thickness of 0.75 inches (19.05 mm), while a Standard 2 inch Class 2500 flange will have an outside diameter of 9.25 inches (234.95 mm) and a thickness of 2 inches (50.80 mm). In addition, the bolt requirement doubles from 4 bolts to 8 bolts, the diameter of the required bolts increases from 0.625 inches (15.88 mm) to 1 inch (25.4 mm), and the applied torque increases from 80 Ft/lbs (108.47 Nm) to 300 Ft/lbs (406.75 Nm). The large diameter and thickness of the Class 2500 flange is required simply to accommodate the 8 large bolts required to meet the recommended torque. Customers are therefore paying a huge amount of money for material consumed in the production of a flanged product in order to accommodate higher pressure uses. The opportunity for unnecessary waste and associated cost is multiplied considerably when dealing with more expensive grades of material, such as alloy 625, which is 10 times more expensive than regular stainless steel. In addition, there are further costs associated with the packaging, transportation and installation of goods that are larger and/or heavier than they need to be, as well as the obvious health and safety implications. There is therefore a need for improved flange solutions which reduces or eliminates the effect of one or more of the issues identified above. According to a first aspect of the invention, there is provided a mechanical seal assembly, in accordance with claim 1.

In use, it will be understood that the metal-to-metal seal is created by bringing the two flanges together, such that each annular seal surface of said metallic seal element engages with the annular metallic seal surface of a respective one of said first and second flanges (e.g. with the respective central bores of the two flanges in concentric alignment with one another). Bolts are then used (via the bolt holes) to secure the first and second flanges together and bring about sealing engagement between the annular seal surfaces of the metallic seal element and the annular metallic seal surfaces of said first and second flanges.

The seal assembly in accordance with the invention provides a more robust sealing solution than known gasket arrangements for standard flanges of the kind set forth. It also drastically reduces the amount of bolting force required to maintain the seal than would otherwise be necessary for a gasket solution using the same standard flange geometry.

In general, the forces required to energise the metallic seal will be much lower than those required in gasket solutions, thereby reducing the need for complex bolting solutions for high pressure applications. As a result, small standard flanges (e.g. having a 'small' flange geometry typically associated with low pressure applications) can be converted to operate at high pressures (i.e. substantially above their standard rated value. Moreover, the use of the recess has been found to reduce bending stresses within the flange body under bolt torque, thereby making it more likely that small standard flanges can be bolted to operate at higher pressures than is conventionally accepted under known operating standards. In exemplary embodiments, the first and/or second flange body is connected to or connectable to a pipe, e.g. by a weld or a screw thread.

In exemplary embodiments, the annular metallic seal surface of each flange body defines a transition between said recess and said fluid bore.

In exemplary embodiments, the bottom surface of each recess extends orthogonal to said central axis. In exemplary embodiments, the flange connection face of each flange includes an upstand, concentric with said fluid bore, having a mating surface for abutment with the mating surface of another respective flange, i.e. when two such flanges are brought together. In exemplary embodiments, the flange connection face of each flange includes an outer radial surface, outboard of said upstand, wherein the outer radial face is offset axially from said mating surface.

In exemplary embodiments, the bottom face of the recess in each flange is offset axially from the outer radial surface of said flange.

In exemplary embodiments, at least one of said flanges is a standard flange, of the kind set forth, e.g. having a flange body with first and second ends and a fluid bore of circular cross section extending between the first and second ends, wherein a first end of the fluid bore is exposed at the first end of the flange body, wherein the first end of the flange body is of larger diameter than the second end of the flange body and defines a flange connection face concentric with the fluid bore, and wherein a plurality of bolt holes are provided through the first end, off-set from the fluid bore and extending in a direction parallel with the central axis of the fluid bore; and further wherein the recess has been formed in the flange connection face of said standard flange (e.g. by removing material from the flange connection face). In exemplary embodiments, the standard flange is of the kind wherein the flange connection includes an upstand, concentric with said fluid bore, having a mating surface for abutment with the mating surface of another respective flange (e.g. when two such flanges are brought together), and wherein the flange connection face includes an outer radial surface, which is outboard of said upstand and offset axially from said mating surface; and further wherein at least a part of the recess has been formed by removing stock from said upstand.

In exemplary embodiments, the standard flange has been modified such that the bottom face of the recess in said flange is offset axially from the outer radial surface of said flange.

In exemplary embodiments in which one or more standard flanges are used, having said recess machined therein, it will be understood that the metallic seal element will be designed such that the annular seal surface on each of the first and second faces of said metallic seal element is complimentary to the new annular metallic seal surface_of the or each flange.

In exemplary embodiments, the metallic seal surface extends at an angle to said central axis of the fluid bore.

In exemplary embodiments, the metallic seal surface extends from a first diameter at said surface spaced axially from said flange connection face to a second diameter at a further depth within the flange body, wherein the first diameter is greater than the second diameter.

In exemplary embodiments, a shoulder is formed between the metallic seal surface and an internal wall of the fluid bore on each flange. In exemplary embodiments, the shoulder is located at a depth from the flange connection face of each flange suitable to ensure that the seal element is spaced therefrom when the seal element is arranged in sealing engagement between the first and second flanges. In exemplary embodiments, the seal element is configured so that the central bore thereof confirms at least substantially to the dimensions of the fluid bore of the first and second flanges. In exemplary embodiments, each of the annular seal surfaces of the metallic seal element are part of a cone, lip, nose or other projection extending from a respective face of the metallic seal element.

In exemplary embodiments, the first and/or second flange is a weld neck flange, e.g. ANSI B 16.5 Class 150 weld neck flange.

The invention also has application in the provision of a metal-to-metal seal between a single flange of (whether of standard configuration and then modified to include the recess and a new metallic seal surface, or specifically-produced as a bespoke item with the recess and metallic seal surface as an integral part thereof) and an auxiliary device having a flanged connection face configured for bolted connection with the single flange. In such applications, it will be understood that the flanged connection face of the auxiliary device will already include a seat surface for use in clamping a gasket between the flanged connection face of the auxiliary device and the flange connection face of the single flange. Accordingly, the seat surface of the auxiliary device can be modified to include a complimentary recess and metallic seal surface (or, indeed, the auxiliary device may be produced as a bespoke item, with the recess and metallic seal surface as an integral part thereof. The metallic seal element will therefore be designed so that the annular seal surface on one face thereof is complimentary to the new metallic seal surface of the single flange, and so that the annular seal surface on the other face thereof is complimentary to the metallic seal surface of the auxiliary device, for sealing engagement therewith. Metal-to-metal seals can then be created between by clamping the metallic seal element between the single flange and the auxiliary device, by arranging the metallic seal element so that each annular seal surface of said metallic seal element engages with a metallic seal surface on a respective one of said single flange and said auxiliary device, and then using bolts or the like to secure the assembly together and bring about sealing engagement between the annular seal surfaces of the metallic seal element and the metallic seal surfaces of said single flange and auxiliary device.

A standard flange of the kind set forth means a flange of known configuration in the art, comprising a flange body having first and second ends and a fluid bore of circular cross section extending between the first and second ends, wherein a first end of the fluid bore is exposed at the first end of the flange body, wherein the first end of the flange body is of larger diameter than the second end of the flange body and defines a flange connection face concentric with the fluid bore, and wherein a plurality of bolt holes are provided through the first end, off-set from the fluid bore and extending in a direction parallel with the central axis of the fluid bore.

Although the illustrated embodiments herein have been designed using ANSI B 16.5 as the baseline geometry, the invention clearly applies to any range of flange family defined by an international standard using traditional raised face or RTJ compressed gaskets. Such families will include different sizes of flange grouped by pressure rating and having increasingly large and complex bolting configurations as the pressure range increases. The following are typical examples of international standards for flanges to which the invention will have applicability: ANSI B16.5, ANSI B 16.47, BS3293, BS1560, EN1092, BS4504, DIN SERIES, NFE SERIES, API FLANGES, BS10, HS, and ISO 7005.

As mentioned above, a single flange can be used to create a seal with an auxiliary device having a flanged connection face (i.e. configured for bolted connection and communication with the first end of the flange), by clamping a metallic seal element therebetween. A wide range of OEM auxiliary devices can be modified to take advantage of the enhanced performance, reduced weight and simplified bolting arrangements that the invention facilitates, particularly those made for flanged connection incorporating standard flange geometry derived from ANSI B 16.5 (or any other international standard), integral or otherwise. Examples of OEM manufacturer currently active in producing such devices include Flexsteel pipe, Swagelok (RTM), Parker Hannifin, Rosemount (RTM), Emerson, Oliver Valves, President Engineering, Weir, Adanac, Cameron, Schlumberger, Shipham, Schnieder, Alco Hi Tech, Endress and Hauser. AES Seal, and Rotorke. Examples of the kind of auxiliary device to which the invention can be applied include valve products such as ball valves, gate valves, globe valves, diaphragm and pinch valves, plug and ball valves, butterfly valves, needle valves, as well as specifically designed products such as process interface and instrumentation valves, valve products such as mono flanges and block & bleed valves. Further specific examples of OEM product include Parker Pro Bloc (RTM), Alco Sub Star needle valves, Swagelok (RTM) mono flanges or block & bleed valves. The invention will also have application in pressure, level and flow products (wireless or otherwise), such as Rosemount Tank Radar products and British Rototherm (RTM) products.

Further advantageous features or aspects of the invention are set out in the dependent claims, and/or will be apparent from the following description of embodiments, made by way of example with reference to the accompanying drawings, in which:

Figure 1 is a perspective view of a conventional weld neck flange;

Figure 2 is a perspective view of a modified weld neck flange; Figure 3 is a cross-section through a weld neck flange sealing assembly, incorporating the modified weld neck flange of Figure 2 and a metallic sealing element;

Figure 4A is an enlarged view of part of the assembly of Figure 3 in a first state, prior to bolting;

Figure 4B is an enlarged view of part of the assembly of Figure 3 in a second state, after bolting;

Figure 5 is similar to Figure 3, showing a cross-section through a variant weld neck flange sealing assembly, incorporating the modified weld neck flange of Figure 2 and an auxiliary device; and Figure 6 is similar to Figure 3, incorporating a variant of the modified weld neck flange of Figure 2, having fixing points formed in the sealing element and the recess in the flange. The preceding discussion of the background to the invention is intended only to facilitate an understanding of the invention. It should be appreciated that the discussion is not an acknowledgement or admission that any of the material referred to was part of the common general knowledge as at the priority date of the application. Throughout the description and claims of this specification, the words "comprise" and "contain" and variations of the words, for example "comprising" and "comprises", mean "including but not limited to", and is not intended to (and does not) exclude other components, integers or steps. Throughout the description and claims of this specification, the singular encompasses the plural unless the context otherwise requires. In particular, where the indefinite article is used, the specification is to be understood as contemplating plurality as well as singularity, unless the context requires otherwise. Features, integers or characteristics, and compounds described in conjunction with a particular aspect, embodiment or example of the invention are to be understood to be applicable to any other aspect, embodiment or example described herein unless incompatible therewith. The figures are not necessarily to scale.

Referring now to Figure 1, a flange of standard configuration in the art is shown at 10. Accordingly, the flange 10 takes the form of a flange body 12 having first and second ends 14, 16 and a fluid bore 18 of circular cross section extending between the first and second ends 14, 16. A first end of the fluid bore 18 is exposed at the first end 14 of the flange body 12. The first end 14 of the flange body 12 is of larger diameter than the second end 16, and defines a flange connection face 22 concentric with the fluid bore 18. A plurality of bolt holes 24 are provided through the first end of the flange body 12, off-set from the fluid bore 18 and extending in a direction parallel with a central axis 26 of the fluid bore 18.

The illustrated embodiment is based on standard ANSI B16.5 geometry, wherein the flange connection face 22 includes an upstand 20 at the first end of the body 12, having an upper surface 21 extending in a direction orthogonal to the central axis 26.

It will be understood that a conventional flanged joint can be made by bolting together two standard flanges 10, with a compressible gasket (not shown) clamped between the flange connection faces 22 of the two flanges 10 to provide a pressure seal, e.g. wherein the gasket has a body which is clamped between the opposing upstands 20. However, it has been found that the rated values for any given standard flange can be safely and significantly exceeded, if the flanges are modified in accordance with the following method, described with respect to Figures 2 to 5.

Firstly, each flange 10 is modified to define a recess 50 adjacent the flange connection face 22, e.g. as shown in Figure 2. The recess 50 includes a bottom surface 52 spaced axially from said flange connection face 22. Furthermore, each flange 10 is modified to include an annular metallic seal surface 28 extending inwardly from the bottom surface 52 in the direction of said fluid bore 18. The metallic seal surface 28 is concentric with the central axis 26.

In the embodiment of Figures 2 and 3, at least a part of the recess 50 is formed by removing material from a part of the upstand 20 at the first end of the body 12. For example, the recess 50 can be achieved by machining into each upstand 20 or flange connection face 22, and the metallic seal surface 28 can be created by machining a chamfer or other angled transition between the bottom surface 52 and the fluid bore 18. In alternative embodiments, the flange 10 can be a newly formed component (e.g. not necessarily a standard flange), integrally formed with the recess 50 and angled seal surface 28, or the flange 10 may be integrally formed with the recess 50 and the angled seal surface 28 can then be produced by a retro-machining operation. In exemplary embodiments (such as is illustrated in Figure 2), the metallic seal surface 28 extends at an angle to the central axis 26 of the flange body 12, and/or to the bottom surface 42 and/or the flange connection face 22.

In exemplary embodiments (such as is illustrated in Figure 2), the metallic seal surface 28 extends at an angle to the central axis 26 of the fluid bore 18, from a first diameter at said bottom surface 42 to a second diameter at a depth within the flange body 12 (i.e. spaced from the bottom surface 40), wherein the first diameter is greater than the second diameter.

In exemplary embodiments (such as is illustrated in Figure 2), a shoulder 29 is provided at a transition between the metallic seal surface 28 and an internal wall 30 of the fluid bore 18. The shoulder 29 is concentric with the central axis 26 of the body 12. In preferred embodiments, the shoulder 29 extends radially, e.g. parallel with the flange connection face 22.

A metallic seal element 32 can then be provided, as shown in Figure 3. The metallic seal element 32 takes the form of a circular band having first and second faces 36, 38 and a central bore 40 therethrough. Each of the first and second faces 36, 38 includes an annular seal surface 42 concentric with the central bore 40. In preferred embodiments, each of the annular seal surfaces 42 of the metallic seal element 32 are part of a lip, nose or other projection extending from a respective face of the metallic seal element, and intended to be energised (e.g. by elastic deformation thereof) in order to bring about a satisfactory metal-to-metal seal with each of the flanges 10. In the illustrated embodiment, the metallic seal element can be said to define a cone projecting from each of said faces, wherein each annular seal surface 42 is defined by an outer surface of a respective cone. The metallic seal element 32 is designed such that the annular seal surface 42 on each of the first and second faces 36, 38 is generally complimentary to the metallic seal surfaces 28 of a respective one of the two flanges 10. If the flanges 10 are identical, the metallic seal surfaces 28 may be of identical shape and configuration. Metal-to-metal seals can then be created between the metallic seal element 32 and the two flanges 10, by locating the metallic seal element 32 between the two flanges 10, such that each annular seal surface 42 engages with the new metallic seal surface of a respective one of said two flanges 10, e.g. as shown in Figure 3. Bolts (not shown) can then be used to secure the two flanges 10 together and bring about sealing engagement between the annular seal surfaces 42 and the metallic seal surfaces 28. The seal surface 42 is configured for energisation (e.g. by elastic deformation) under load (e.g. when the first and second flanges 10 are bolted together through bolt holes 24 aligned in the position shown in Figure 3).

In the illustrated embodiment, the shoulder 29 is located at a depth from the flange connection face 22 suitable to ensure that the seal element 32 is spaced slightly therefrom when the seal surface 42 on the seal element 32 is in sealing engagement with a respective seal surface on the flange 10.

In the illustrated embodiment, the seal element 32 is configured so that the central bore 40 conforms at least substantially to the dimensions of the fluid bore 18 of the flanges 10, in order to provide fully flush bore operating conditions between the two flanges 10, in use, thereby reducing flow inefficiencies. This contrasts with conventional gasket arrangements, where the gasket bore typically has a much greater diameter than the fluid bore on each flange forming the sealed connection.

Moreover, in exemplary embodiments (such as illustrated herein), the seal element 32 defines an annular rib extending outboard of the annular seal surfaces 42, the annular rib having opposing radial faces. The seal element 32 and/or the flanges 10 are configured such that the opposing radial surfaces of the rib are spaced from the bottom surface 52 of a respective recess 50, when the metallic seal element 32 is clamped between the first and second flanges 10. This can be seen most clearly in Figures 4A and 4B. Moreover, the annular rib defines an outer side wall 54, and the recess 50 in each flange body 12 has a peripheral wall 56 configured to surround (but be spaced from, in exemplary embodiments) a portion of said outer side wall 54 when the seal element 32 is clamped between the first and second flanges 10, e.g. as shown in Figures 3. In effect, the rib can be said to be floating within a compartment defined by the two recesses 50, when the two flanges 10 are brought together, since the seal element 32 does not bear against any part of the recesses 50. In exemplary embodiments, one or both of the flanges 10 may include an internal passageway (not shown) having an inlet at a side surface of the flange body 12 and an outlet at the bottom surface 52 of the recess 50 for use in reverse integrity testing the sealing performance of the assembly. Accordingly, the seal element 32 may also include an aperture extending through the annular rib (e.g. between said opposing radial surfaces thereof).

As mentioned above, the flange body includes an upstand 20, the upper surface of which defines a mating surface 21, concentric with said fluid bore 18, outboard of said recess 50, and configured such that the mating surface 21 of the first flange 10 and the mating surface 21 of the second flange 10 engage in frictional contact with one another, when the seal element 32 has been securely clamped between the first and second flanges 10 (e.g. using bolts or the like via the bolt holes 24). As can be seen clearly in Figures 4A and 4B, the flange connection face 22 of each flange 10 includes an outer radial surface 58, outboard of said upstand 20. The outer radial face 58 is offset axially from said mating surface 21 (i.e. at a depth below the mating surface 21). Moreover, bottom surface 52 of the recess 50 in each flange 10 is offset axially from the outer radial face 58 of said flange (i.e. at a depth below the outer radial face 58). This can be seen most clearly in Figures 4A and 4B. In exemplary embodiments, the mating surfaces 21 are configured to create a secondary test seal when the two flanges 10 are brought together for fluid communication with the seal element 32 securely clamped therebetween (e.g. using bolts or the like via the bolt holes 24). Figures 4 A and 4B show an exemplary embodiment in which each mating surface 21 defines a taper or slope on the flange connection face, wherein the height of the upstand decreases from a radially inner edge 70 to a radially outer edge 72. The effect is that the mating surfaces define a substantially V-shaped recess 74 (albeit open at both ends, in the particular embodiment illustrated in Figure 4A). As bolts or the like are used to secure the two flanges 10 together, via bolt holes 24, any clearance between the opposing mating surfaces 21 at the radially inner edges 70 is taken up, and the radially outer edges 74 are pulled in the direction of one another, in order to substantially take up any clearance, and thereby ensure a suitable seal between the opposing mating surfaces 21, e.g. as shown in Figure 4B.

In exemplary embodiments, the first and/or second flange body 12 is connected to or connectable to a pipe, e.g. by a weld or a screw thread.

It will be understood that the flanges 10 in Figures 1 to 3 are of the kind known as weld neck flanges. However, the invention has application for other types of flange or device having a flanged connection face. An example of such a device is illustrated in Figure 5, wherein the device 60 has a flanged connection face 62 or seat configured for bolted connection with a flange of standard configuration. In such applications, it will be understood that the flanged connection face 62 of the auxiliary device 60 will already include a seat surface 64 for use in clamping a conventional gasket between the flanged connection face 62 of the auxiliary device 60 and the flange connection face 22 of the flange. Accordingly, the invention can be modified, so that a recess 50 and metallic seal surface 28 (e.g. of the kind shown in Figure 2) is provided in the flange connection face 22 of the flange 10 (e.g. in the manner already set forth), as well as in the flanged connection face 62 of the auxiliary device 60. The metallic seal element 32 will therefore be designed so that the annular seal surface 42 on one face thereof is complimentary to the new metallic seal surface 28 of the flange 10, and further so that the annular seal surface 42 on the other face thereof is complimentary to the metallic seal surface 28 of the auxiliary device 60. Metal-to-metal seals can then be created between said metallic seal element 32 and each of said flange 10 and auxiliary device 60, by arranging the metallic seal element 32 so that each annular seal surface 42 of said metallic seal element 32 engages with a metallic seal surface 28 of a respective one of said flange 10 and auxiliary device 60, and then by using bolts or the like, via the bolt holes 24, to secure them together and bring about sealing engagement. Again, a shoulder 29 may be provided on the auxiliary device 60, located at a depth from the connection face 64 suitable to ensure that the seal element 32 is spaced therefrom when the seal surface 42 on the seal element 32 is in sealing engagement with the seal surface 28 on the device 60. It will be understood that the seal element 32, and/or the flange 10 and/or the auxiliary device 60 may be configured to ensure a clearance between the rib of the seal element 32 and a compartment defined by cooperation between the recesses on the flange and auxiliary device.

Figure 6 shows an adaptation that may be applied to one or more of the embodiments described and illustrated herein. In particular, the bottom surface 52 of the recess 50 on at least one of the flanges 10 may be provided with a plurality of apertures 66 configured for receiving a fastener 68, such as a screw or the like, for use in locating the seal element 32 in correct alignment with the central axis 26 of the fluid bore 18. Accordingly, similar apertures 67 are required through the seal element (e.g. at locations outboard of the seal surface 42). The seal element 32 is not necessarily clamped against the seal surface 28 of the flange by the fastener, and instead may be allowed a degree of axial travel with respect to the flange, at least until such time as it becomes clamped in place by the opposing flange 10 (or auxiliary device 60, in embodiments of the kind described with reference to Figure 5). As mentioned, this kind of arrangement allows for correct centring of the seal element 32, and can be used to avoid disturbance of the seal element (e.g. by clash with the opposing flange body or auxiliary device) during installation. This has particular advantage when dealing with heavy and/or large diameter flanges, also reducing handling and safety issues). This is possible by virtue of the fact that the annular rib of the seal element is not in active use during sealing, whereas other types of sealing arrangement (e.g. such as gaskets) require compression of the rib or its structural equivalent.

In exemplary embodiments, the metallic seal element is made from carbon steel, stainless steel or nickel alloy material. In exemplary embodiments, the material should have mechanical properties suitable to provide a suitable yield strength for the pressures intended, as well as providing suitable corrosion resistance (since the seal element will be in contact with a working fluid, in use). In exemplary embodiments, the flange is made from carbon steel, stainless steel or nickel alloy material.

Although the illustrated flange embodiments have been designed using ANSI B 16.5 as the baseline geometry, the invention clearly applies to any range of flange family defined by an international standard using traditional raised face or RTJ compressed gaskets. Such families will include different sizes of flange grouped by pressure rating and having increasingly large and complex bolting configurations as the pressure range increases. The following are typical examples of international standards for flanges to which the invention will have applicability: ANSI B16.5, ANSI B16.47, BS3293, BS1560, EN1092, BS4504, DIN SERIES, NFE SERIES, API FLANGES, BS10, JIS, and ISO 7005.