Fluid fitting with bearing sleeve

Abstract

A fluid fitting includes a coupling body having a coupling passageway and an attachment portion having at least one seal, wherein the coupling passageway defines a coupling body axis; a bearing sleeve having a sleeve passageway that defines a sleeve axis; and a drive ring having a ring passageway that defines a ring axis. The fluid fitting is configured to be mechanically attached to a fluid element by arranging the fluid element within the coupling passageway, arranging the coupling body and bearing sleeve within the ring passageway of the drive ring, and axially moving the drive ring relative to the bearing sleeve and coupling body such that the drive ring applies a compressive force to the coupling body sufficient to cause the at least one seal of the coupling body to bite into and permanently deform the fluid element, thereby mechanically attaching the coupling body to the fluid element.

Description

FLUID FITTING WITH BEARING SLEEVEPLACE HOLDER CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims the benefit of U. S. provisional application Serial No.63 / 779,919 filed March 28, 2025, the contents of which are incorporated by reference.FIELD OF THE DISCLOSURE

[0002] The present disclosure generally relates to a fluid fitting and, more particularly, to a fluid fitting with a bearing sleeve.BACKGROUND

[0003] Various types of fittings have been developed for joining tubes and pipes to other tubes and pipes, or to other fluid apparatus such as pumps, fluid motors, actuation cylinders, etc. For thin-walled tubing or pipe, various types of fittings are used which compress against the outside diameter of the tube or pipe to create a seal. One particular type of such a fitting includes a drive ring which is forced over a coupling body to compress it radially inwardly against the tube or pipe to create a seal. Generally, this type of fitting has one or more circumferential coupling elements (e.g., teeth or ridges) on the inside diameter of its coupling body which, when compressed inwardly by a drive ring, engage the outside diameter of the tube or pipe to create one or more leak-tight mechanical connections or joints between the tube or pipe and the fitting. This engagement of the coupling elements of the fitting with the tube or pipe causes the pipe to be deformed radially inwardly, with the coupling body of the fitting located externally about the tube or pipe.

[0004] Examples of such mechanically attached fittings are provided in U. S. Pat. Nos.4,482,174; 5,110,163; 5,114,191; 6,692,040; and 7,575,257. One example installation tool employable for attaching these types of fittings to a tube or pipe is described in U. S. Pat. No. 5,305,510. All the teachings and substance of these patents are hereby expressly incorporated by reference into the present application.BRIEF DESCRIPTION OF THE DRAWINGS

[0005] FIG. l is a cross-sectional view of an example fluid fitting for a fluid element;

[0006] FIG. 2 is an enlarged partial cross-sectional view of a coupling body of the fluid fitting;

[0007] FIG. 3 is an enlarged partial cross-sectional view of a bearing sleeve of the fluid fitting;

[0008] FIG. 4 is an enlarged partial cross-sectional view of a drive ring of the fluid fitting;

[0009] FIG. 5 is an enlarged partial cross-sectional view of the coupling body and bearing sleeve in a joined configuration; and

[0010] FIG. 6 is an enlarged partial cross-sectional view of the fluid fitting in a preinstalled configuration with the fluid element extending into a passageway of the coupling body.DETAILED DESCRIPTION

[0011] The following is a detailed description of illustrative embodiments of the present application. As these embodiments of the present application are described with reference to the aforementioned drawings, various modifications or adaptations of the methods and or specific structures described may become apparent to those skilled in the art. All such modifications, adaptations, or variations that rely upon the teachings of the present application, and through which these teachings have advanced the art, are considered to be within the spirit and scope of the present application. Hence, these descriptions and drawings are not to be considered in a limiting sense as it is understood that the present application is in no way limited to the embodiments illustrated. Moreover, certain terminology is used herein for convenience only and is not to be taken as a limitation. Still further, in the drawings, the same reference numerals are employed for designating the same elements.

[0012] Furthermore, the term “substantially” is intended to note that the described features are equal or approximately equal to a value or characteristic, as desired, reflecting tolerances, conversion factors, rounding off, measurement error and the like, and other factors. The term is also utilized herein to represent the degree by which a quantitative representation may vary from a stated reference without resulting in a change in the basic function of the subject matter at issue. For example, as used herein, the term “substantially” can denote values or characteristics that are within about 10% of exact, for example within about 5% of exact, or within about 2% of exact. When the term “substantially” is used in describing a value or characteristic, the disclosure should be understood to include the exact value or characteristic being referred to.

[0013] Turning to FIG. 1, an example fluid fitting 10 is shown that can be joined to a fluid element 12, wherein the fluid fitting 10 and fluid element 12 can be arranged relative to alongitudinal axis Lthat defines a first axial direction Di and a second axial direction D2 opposite to the first axial direction Di. For the purposes of this disclosure, a “fluid element” can be any structure (e.g., pipe, tube, manifold, fluid connector, nozzle, etc.) defining a passageway for conveying fluid therethrough. For example, the fluid element 12 in the present embodiment is a pipe defining a pipe passageway 14 extending therethrough, wherein the pipe passageway 14 has a central axis Xi. The pipe can be one of a schedule 10 type pipe through a schedule 80 type pipe, having a wall thickness between about 0.057 inches to about 0.261 inches. As another example, the fluid element 12 can be outside diameter-dimensioned tubing having wall thicknesses ranging from 0.035 inches through 0.109 inches.

[0014] The fitting 10 includes a coupling body 16, a bearing sleeve 18, and a drive ring 20 that respectively define a coupling passageway 26, a sleeve passageway 28, and a ring passageway 30 extending therethrough, wherein each passageway 26, 28, 30 has an associated central axis X2, X3, X4. Moreover, the fluid element 12 and the components 16, 18, 20 of the fitting 10 can be arranged relative to the longitudinal axis L as shown in FIG. 1, such that the central axes Xi, X2, X3, X4 of the fluid fitting 10 and fluid element 12 are substantially colinear with each other and the longitudinal axis L.

[0015] In the present example, the coupling body 16 and the drive ring 20 are formed of stainless steel, and the bearing sleeve 18 is formed of polytetrafluoroethylene (PTFE). However, the coupling body 16 and drive ring 20 could alternately be formed of any of a variety of other fitting materials including, for example, carbon steel, 90 / 10 copper nickel, 70 / 30 copper nickel, etc. Moreover, the bearing sleeve 18 could be formed of other pliable materials such as, for example, acetal, nylon, or materials with other polymeric compounds (e.g., synthetic flouropolymers).

[0016] It is to be appreciated that the features of each component 12, 16, 18, 20 in the present embodiment generally extend circumferentially and symmetrically about the component’s associated axis Xi, X2, X3, X4. As used herein, the terms “axial”, “radial”, “circumferential”, and the like when describing features of a component 12, 16, 18, 20 are relative to the component’s associated axis Xi, X2, X3, X4. Moreover, the terms “proximal”, “distal”, “inboard”, “outboard”, and the like are used to indicate directions or relative placements of structure along the component’s associated axis Xi, X2, X3, X4. For example, the first axial direction Di in FIG. 1 corresponds to an inboard or proximal direction for each component 12, 16, 18, 20, wherein afirst structure is proximal or inboard to a second structure if the first structure is placed downstream of the second structure in the first axial direction Di. Meanwhile, the second axial direction D2 in FIG. 1 corresponds to an outboard or distal direction for each component 12, 16, 18, 20, wherein a first structure is distal or outboard to a second structure if the first structure is placed downstream of the second structure in the second axial direction D2.

[0017] The coupling body 16 comprises an attachment portion 32 having a proximal end 34, a distal end 36, and inner and outer surfaces 38, 40 that extend from the proximal end 34 to the distal end 36. The inner surface 38 of the attachment portion 32 at least partially defines the coupling passageway 26 of the coupling body 16. Moreover, the coupling body 16 comprises a circumferential flange 42 at the proximal end 34 of the attachment portion 32 that extends radially outward from the outer surface 40. The flange 42 defines a tool engaging surface 46, which extends in the radial direction and can be used by an external installation tool to join the fluid fitting 10 to the fluid element 12, as described later herein.

[0018] Further details of the fluid fitting 10 will now be described with reference to FIGS. 2-6. Notably, FIGS. 2-4 respectively show the coupling body 16, bearing sleeve 18, and drive ring 20 in their uninstalled configurations in which those elements are isolated and separate from each other. More specifically, in their uninstalled configurations, the passageways 26, 28, 30 of the coupling body 16, bearing sleeve 18, and drive ring 20 are open passageways that do not receive any structure therethrough. Meanwhile, FIG. 5 shows the coupling body 16 and bearing sleeve 18 in a joined configuration in which the sleeve passageway 28 of the bearing sleeve 18 receives the attachment portion 32 of the coupling body 16. Finally, FIG. 6 shows the fluid fitting 10 in a pre-installed configuration in which the ring passageway 30 of the drive ring 20 receives the coupling body 16 and bearing sleeve 18 in their joined configuration.

[0019] With reference to FIG. 2, the inner surface 38 of the coupling body 16 defines a plurality of circumferential seals 50, 52, 54 including an outboard or distal seal 50, a main seal 52, and an inboard or proximal seal 54. Each seal 50, 52, 54 can comprise one or more teeth that extend radially inward from neighboring portions of the inner surface 38 for sealing between and mechanically connecting the coupling body 16 to the fluid element 12. For example, in the present embodiment, the main seal 52 comprises a pair of twin teeth slightly separated by an annular groove. Meanwhile, the inboard and outboard seals 50, 54 each comprise a single tooth.

[0020] The inner surface 38 of the coupling body 16 also defines a circumferential anti-torsion ridge 60 (also referred to herein as a torsion ridge) that is proximal to the outboard seal 50 and is configured to resist torsion loads between the coupling body 16 and fluid element 12. The torsion ridge 60 likewise extends radially inward from neighboring portions of the inner surface 38, and preferably has friction surfaces 62 formed on its land (e.g., by knurling, broaching, or the like) to better resist torsion loads between the coupling body 16 and the fluid fitting 12 once attached together.

[0021] The outer surface 40 of the coupling body 16 comprises a plurality of outer surface portions 40a-i including an abrupt-upsloping surface portion 40a, a ribbed surface portion 40b, a diametrically-constant surface portion 40c, an abrupt-upsloping surface portion 40d, a plateau surface portion 40e, a gradually-downsloping surface portion 40f, a gradually-upsloping surface portion 40g, a plateau surface portion 40h, and a gradually-downsloping surface portion 40i, which are arranged successively along the inboard direction Di. The upsloping surface portions 40a, 40d, and 40g each have an outer diameter that increases along the coupling body axis X2 toward the proximal end 34 of the attachment portion 32, whereas the downsloping surface portions 40f, 40i each have an outer diameter that decreases along the coupling body axis X2 toward the proximal end 34. In particular, the slope / angle of the surface portions 40f, 40g, 40i (relative to the coupling body axis X2) gradually changes along the coupling body axis X2, whereas the slope / angle of the surface portions 40a, 40d is substantially constant along the coupling body axis X2. Moreover, the surface portion 40c has an outer diameter that is substantially constant along the coupling body axis X2.

[0022] The surfaces portion 40d-f of the outer surface 40 collectively define a main compression land 66 of the attachment portion 32, wherein the plateau surface portion 40e of the main compression land 66 is directly opposite to the main seal 52 in the radial direction.Moreover, the surface portions 40g-i of the outer surface 40 collectively define an inboard compression land 68 of the attachment portion 32, wherein the plateau surface portion 40b of the inboard compression land 68 is directly opposite to the inboard seal 54 in the radial direction. The configuration of these lands 66, 68, particularly their upsloping surface portions 40d, 40g, can assist in driving the main and inboard seals 52, 54 into the fluid element 12.

[0023] The ribbed surface portion 40b of the outer surface 40 defines a plurality of outwardfacing circumferential ribs 70 (e g., sharp ridges, rounded protuberances, etc.) separated fromone another by outer circumferential grooves 72. The ribs 70 are configured to inhibit the bearing sleeve 18 and drive ring 20 from slipping or working off the coupling body 16 in the outboard direction D2 once they are installed on the coupling body 16. Moreover, the abrupt-upsloping surface portion 40a provided at the distal end 36 of the attachment portion 32 assists in initially installing the bearing sleeve 18 and drive ring 20 onto the coupling body 16. Preferably, the surface portion 40a extends at an angle (relative to the coupling body axis X2) that is from 15° to 25°, and more preferably about 20°. Notably, the abrupt-upsloping surface portion 40d can extend at a substantially similar angle relative to the coupling body axis X2. However, the surface portions 40a, 40d may extend at other angles that are similar to or different from each other without departing from the scope of the disclosure.

[0024] Turning to FIG. 3, the bearing sleeve 18 is a generally cylindrical body of pliable material (e.g., PTFE) having a distal sleeve portion 18a that defines a distal end 76 of the bearing sleeve 18, a proximal sleeve portion 18d that defines a proximal end 78 of the bearing sleeve 18, and an intermediate portion 18b, 18c that connects the proximal and distal sleeve portions 18a, 18d, wherein the intermediate portion 18b, 18c comprises a ribbed sleeve portion 18b and a cylindrical sleeve portion 18c. In the present example, a wall thickness (measured in the radial direction) of the bearing sleeve 18 is substantially constant along the bearing sleeve axis X3. Preferably, the wall thickness of the bearing sleeve 18 is from 0.005” to 0.020”, and more preferably about 0.010”. However, the bearing sleeve 18 may have other wall thicknesses that may or may not be constant along the bearing sleeve axis X3 without departing from the scope of the disclosure.

[0025] The bearing sleeve 18 is configured to conform to the outer surface 40 of the coupling body 16. For example, the distal sleeve portion 18a of the bearing sleeve 18 is configured to conform to the abrupt-upsloping surface portion 40a of the coupling body 16. In particular, the distal sleeve portion 18a has an inner diameter and an outer diameter that both increase along the bearing sleeve axis X3 toward the proximal end 78 of the bearing sleeve 18, wherein the slope of the distal surface portion 78a (relative to the bearing sleeve axis X3) is substantially constant along the bearing sleeve axis X3. As noted above, the abrupt-upsloping surface portion 40a of the coupling body 16 extends at an angle (relative to the coupling body axis X2) that is from 15° to 25°, and more preferably about 20°. Accordingly, the inner and outer surfaces of the distal sleeve portion 18a will extend at a substantially similar angle relative to the bearing sleeve axis X3. Thatis, the inner and outer surfaces of the distal sleeve portion 18a will extend at an angle relative to the bearing sleeve axis X3 that is from 15° to 25°, and more preferably about 20°.

[0026] As another example, the ribbed sleeve portion 18b of the bearing sleeve 18 is configured to conform to the ribbed surface portion 40b of the coupling body 16. In particular, an inner surface of the ribbed sleeve portion 18b defines a plurality of inward-facing circumferential ribs 80 (e.g., sharp ridges, rounded protuberances, etc.) separated from one another by inner grooves 82, and an outer surface of the ribbed sleeve portion 18b defines a plurality of outwardfacing circumferential ribs 90 separated from one another by outer grooves 92. The inner ribs 80 of the bearing sleeve 18 are configured to mate with the outer grooves 72 of the coupling body 16, and the outer ribs 70 of the coupling body 16 are configured to mate with the inner grooves 82 of the bearing sleeve 18. Moreover, in the present embodiment, the outer ribs 90 and grooves 92 of the bearing sleeve 18 substantially match the profile of the outer ribs 70 and grooves 72 of the coupling body 16. In this manner, both the inner and outer surfaces of the ribbed sleeve portion 18b conform to the ribbed surface portion 40b of the coupling body 16

[0027] As yet another example, the cylindrical sleeve portion 18c of the bearing sleeve 18 is configured to conform to the diametrically-constant surface portion 40c of the coupling body 16. In particular, the cylindrical sleeve portion 18c has an inner diameter and an outer diameter that are substantially constant along the bearing sleeve axis X3, wherein the inner diameter of the cylindrical sleeve portion 18c is substantially similar to (but slightly larger than) the outer diameter of the diametrically-constant surface portion 40c of the coupling body 16. The inner and outer surfaces of the cylindrical sleeve portion 18c are thus cylindrical surfaces that conform to the diametrically-constant surface portion 40c of the coupling body 16.

[0028] As still yet another example, the proximal sleeve portion 18d of the bearing sleeve 18 is configured to conform to the abrupt-upsloping surface portion 40d of the coupling body 16. In particular, the proximal sleeve portion 18d has an inner diameter and an outer diameter that both increase along the bearing sleeve axis X3 toward the proximal end 78 of the bearing sleeve 18, wherein the slope of the proximal sleeve portion 18d (relative to the bearing sleeve axis X3) is substantially constant along the bearing sleeve axis X3. As noted above, the abrupt-upsloping surface portion 40d of the coupling body 16 can extend at an angle (relative to the coupling body axis X2) that is from 15° to 25°, and more preferably about 20°. Accordingly, the inner and outer surfaces of the proximal sleeve portion 18d will extend at a substantially similar angle relative tothe bearing sleeve axis X3. That is, the inner and outer surfaces of the proximal sleeve portion 18d will extend at an angle relative to the bearing sleeve axis X3 that is from 15° to 25°, and more preferably about 20°.

[0029] The inner and outer surfaces of the bearing sleeve 18 are thus configured to conform to the outer surface 40 of the coupling body 16, particularly the outer surface portions 40a-d of the coupling body 16. In the present embodiment, the bearing sleeve 18 is a semi-rigid body that assumes the shapes and configurations described above in its uninstalled configuration shown in FIG. 3. In other examples, the bearing sleeve 18 can be an elastic body that can radially expand to accommodate the attachment portion 32 of the coupling body 16 within, and will conform to the outer surface 40 of the coupling body 16 as it receives the attachment portion 32, thereby assuming the shapes and configurations described above once the bearing sleeve 18 is joined to the coupling body 16. Moreover, it is to be appreciated that the bearing sleeve 18 can conform to additional, fewer, and / or alternative portions of the coupling body’s outer surface 40 without departing from the scope of the disclosure. For example, the inner surface 78 of the bearing sleeve 18 can include additional portions that conform to the remaining portions 40e-i of the coupling body’s outer surface 40.

[0030] Turning to FIG. 4, the drive ring 20 has a distal end 96, a proximal end 98, and an inner surface 100 that extends from the distal end 96 to the proximal end 98 and defines the ring passageway 30. The inner surface 100 includes a ribbed surface portion 100a, an abrupt upsloping surface portion 100b, a diametrically-constant surface portion 100c, an abrupt upsloping surface portion lOOd, a diametrically-constant surface portion 40e, and an abrupt upsloping surface portion lOOf, which are arranged successively along the inboard direction Di. The upsloping surface portions 100b, lOOd, lOOf have an inner diameter that increases along the drive ring axis X4 toward the proximal end 98 of the drive 20, and the surface portions 100c, lOOe have an inner diameter that is substantially constant along the drive ring axis X4. Moreover, the ribbed surface portion 100a includes a plurality of inward-facing circumferential ribs 110 (e g., sharp ridges, rounded protuberances, etc.) separated from one another by inner grooves 112. Lastly, the drive ring 20 includes a tool engaging surface 116 at its distal end 96 for engagement with the external installation tool, which extends in the radial direction from the ribbed surface portion 100a and can be used to join the fluid fitting 10 to the fluid element 12.

[0031] With reference to FIGS. 5 and 6, an installation process of the fitting 10 onto the fluid element 12 will now be described. As shown in FIG. 5, the coupling body 16 and bearing sleeve 18 can be initially assembled to assume a joined configuration such their axes X2, X3 are substantially colinear and the attachment portion 32 of the coupling body 16 is received within the sleeve passageway 28 of the sleeve 18. As joined, the sleeve portions 18a-d of the bearing sleeve 18 will abut and be radially aligned with the respective outer surface portions 40a-d of the coupling body 16 in the joined configuration. Moreover, the sleeve portions 18a-d will conform to the respective outer surface portions 40a-d. In particular, the inner and outer surfaces of each sleeve portion 18a-d will extend substantially parallel to their associated outer surface portion 40a-d of the coupling body 16, such that the inner and outer surfaces of each sleeve portion 18a-d substantially match the profile of their associated outer surface portion 40a-d. Moreover, the outer ribs 70 of the coupling body 16 will mate with the inner grooves 82 of the bearing sleeve 18, and the inner ribs 80 of the bearing sleeve 18 will mate with the outer grooves 72 of the coupling body 16. This mating of the ribs 70, 80 and grooves 82, 92 will inhibit further movement of the bearing sleeve 18 relative to the coupling body 16 in both the inboard direction Di and outboard direction D2. Additionally, because the outer surface portions 40a, 40d of the coupling body 16 are upsl oping surfaces that abut the respective bearing sleeve portions 18a, 18d of the bearing sleeve 18, this will further inhibit movement of the bearing sleeve 18 relative to the coupling body 16 in the inboard direction Di. Notably, the outer ribs 70 and grooves 72 of the coupling body 16 will also be radially aligned with the outer ribs 90 and grooves 92 of the bearing sleeve 18, respectively.

[0032] Once the coupling body 16 and bearing sleeve 18 have been assembled to assume their joined configuration in FIG. 5, the drive ring 20 can then be assembled onto the coupling body 16 and bearing sleeve 18 as shown in FIG. 6. Specifically, the drive ring 20 can be assembled onto the coupling body 16 and bearing sleeve 18 such that the central axes X2-4 of all three elements 12, 16, 18 are substantially colinear with the longitudinal axis L, and the coupling body 16 and bearing sleeve 18 are received within the ring passageway 30 of the drive ring 20.Moreover, the drive ring 20 can be moved in the inboard direction Di relative to the coupling body 16 and bearing sleeve 18 until the bearing sleeve portion 18a of the bearing sleeve 18 abuts the inner surface portion lOOd of the drive ring 20. This configuration of the fluid fitting 10 shown in FIG. 6 can be referred to as a “preinstalled configuration” of the fluid fitting 10.

[0033] Notably, the diameter of the surface portion lOOe of the drive ring 20 is slightly smaller than the diameter of the surface portion 40c of the coupling body 16, such that an interference fit is formed when the drive ring 20 is axially forced onto the coupling body 16 and bearing sleeve 18 to the preinstalled configuration of FIG. 6. This will cause the bearing sleeve 18 and the attachment portion 32 of the coupling body 16 to contract radially. Additionally, the ribbed sleeve portion 18b of the bearing sleeve 18 may at least partially deform as shown in FIG. 6, such that the outer surface of the ribbed sleeve portion 18b becomes diametrically constant along its sleeve axis X2. Although the bearing sleeve 18 and the attachment portion 32 of the coupling body 16 contract radially in the preinstalled configuration, a sufficient inner diameter is maintained for the inner surface 38 of the coupling body 16 (particularly at the seals 50, 52, 54 and torsion ridge 60) so that the fluid element 12 can be inserted into the coupling passageway 26 of the coupling body 16 with relative ease.

[0034] Through the interference fit, the fitting 10 can be maintained and shipped to customers in the preinstalled configuration, which facilitates ease of use and installation by the ultimate end-users. Moreover, because the bearing sleeve portion 18a of the bearing sleeve 18 faces and abuts the inner surface portion lOOd of the drive ring 20 in the preinstalled configuration, this will help maintain the fitting 10 in its preinstalled configuration by inhibiting further movement of the drive ring 20 relative to the coupling body 16 and bearing sleeve 18 in the inboard direction Di.

[0035] When it is time to attach the fitting 20 to the fluid element 12, the fluid element 12 can be arranged relative to the fitting 20 such that all axes X1-4 of the fluid element 12 and fitting 20 are substantially coaxial with the longitudinal axis L. Moreover, the fluid element 12 can be inserted within the coupling passageway 26 of the coupling body 16 along the inboard direction Di such that the fluid element 12 extends through the torsion ridge 60 and all seals 50, 52, 54 of the coupling body 16. In some examples, the inner surface 38 of the coupling body 16 can have a stop surface portion that is inboard of the seal 54 and can prevent further inboard movement of the fluid element 12 beyond the stop portion. Then, an external installation tool (not shown) can be used to axially force the drive ring 20 along the coupling body 16 and bearing sleeve 18 in the inboard direction Di. One suitable installation tool is described in commonly-owned U. S. Pat. No. 5,305,510, expressly incorporated herein by reference. As will be known and appreciated by those skilled in the art, the installation tool has opposed jaws that can engage the tool engagingsurface sections 46, 116 (see FIG. 1) of the coupling body 16 and drive ring 20 and be actuated to force or press the drive ring 20 toward the flange 42 of the coupling body 16 via a clamping action along the inboard direction Di.

[0036] As the drive ring 20 is driven axially in the inboard direction Di relative to the coupling body 16 and bearing sleeve 18 from the preinstalled configuration show in FIG. 6, its upsloping inner surface portions 100f, 100d, 100b will sequentially engage and slide along various portions of the coupling body 16 and bearing sleeve 18 to incrementally contract those portions in the radial direction, forcing the seals 50, 52, 54 and torsion ridge 60 of the coupling body 16 into deforming contact with the fluid element 12. For example, the upsloping inner surface portions 100d, 100b of the drive ring 20 will sequentially engage and slide over the bearing sleeve portions 18a, 18b of the sleeve 18, thereby incrementally contracting those bearing sleeve portions 18a, 18b (and the coupling body portions radially aligned therewith) such that the outboard seal 50 and torsion ridge 60 bite into the fluid element 12. Moreover, the upsloping inner surface portions 100f, 100d of the drive ring 20 will sequentially engage and slide along the main compression land 66 of the coupling body 16 such that the main seal 52 bites into the fluid element 12. Lastly, the upsloping inner surface portion 100f of the drive ring 20 will engage and slide along the inboard compression land 68 of the coupling body 16 such that the inboard seal 54 bites into the fluid element 12. Eventually, the drive ring 20 will reach a fully installed position in which its inner surface portions 100a, 100c, 100d are respectively aligned with the outboard seal 50, main seal 52, and inboard seal 54 in the radial direction.

[0037] Notably, the installation process described above will cause the fluid element 12 to plastically deform as the seals 50, 52, 54 of the coupling body 16 radially contract and bite into the fluid element 12. The teeth of the seals 50, 52, 54 may themselves also deform, filling any rough or irregular surface imperfections found on the outside of the fluid element 12.Consequently, each seal 50, 52, 54 will form a 360° circumferential, permanent, metal-to-metal non-leaking seal between the fluid element 12 and the coupling body 16.

[0038] In some examples, the coupling body 16 may deform beyond its elastic limit such that the coupling body 16 also is plastically deformed. Moreover, as the drive ring 20 is driven axially over the coupling body 16 and sleeve 18 to its installed position, reaction forces from the coupling body 16 and sleeve 18 will cause the drive ring 20 to elastically expand in the radial direction. Because the drive ring 20 deforms elastically during installation, the drive ring 20 willexert a continuous elastic force against the coupling body 16 and sleeve 18 that is maintained after installation through the life of the fitting 10, thereby preventing release of the metal -to-metal seal between the coupling body 16 and the fluid element 12.

[0039] The present inventors have found that utilizing the bearing sleeve 18 with the fitting 10 as described above can provide various advantages both during and after installation. For example, in addition to the benefits already described above, the bearing sleeve 18 can reduce friction forces against the drive ring 20 as it is driven axially over the coupling body 16, thereby lowering installation loads and permitting the fitting 10 to be used with harder and / or larger fluid elements that would otherwise require installation loads beyond the capacity of an installation apparatus. Furthermore, the bearing sleeve 18 can reduce metal -to-metal contact between the coupling body 16 and drive ring 20, thus reducing the potential for galling or intermetallic corrosion between those elements 16, 22. Still further, the bearing sleeve 18 can deform to fill in surface imperfections and gaps between the coupling body 16 and drive ring 20, thereby reducing the potential for entrapment areas where corrosion from environmental conditions can initiate.

[0040] Lastly, as noted above, the inner ribbed surface 100a of the drive ring 20 will be radially aligned with the outer ribbed surface 40b of the coupling body 16 in the final installed position. Because the bearing sleeve 18 is pliable, it will deform to meander and fill any gaps between the ribs 70, 110 and grooves 72, 112 of the ribbed surfaces 40b, 100a, thereby interlocking the coupling body 16 and drive ring 20 at their ribbed surfaces 40b, 100a to help prevent any further axial movement of the drive ring 20 in the inboard and outboard directions D1, D2.

[0041] The invention has been described with reference to example embodiments. Obviously, modifications and alterations will occur to others upon reading and understanding the preceding detailed description. It is intended that the exemplary embodiments be construed as including all such modifications and alterations insofar as they come within the scope of the appended claims or the equivalents thereof.

Claims

AMENDED CLAIMSreceived by the International Bureau on11 September 2026 (11.09.2026)CLAIMSWhat is claimed is:

1. A fluid fitting for mechanical attachment to a fluid element, the fluid fitting comprising:a coupling body defining a coupling passageway for receiving said fluid element therein, the coupling body comprising an attachment portion having at least one seal for engaging said fluid element, wherein the coupling passageway defines a coupling body axis;a bearing sleeve defining a sleeve passageway for receiving the attachment portion of the coupling body, wherein the sleeve passageway defines a sleeve axis; anda drive ring defining a ring passageway for receiving the coupling body and bearing sleeve therein, wherein the ring passageway defines a ring axis, wherein the fluid fitting is in an uninstalled configuration in which the coupling body, bearing sleeve, and drive ring are separated from each other, and wherein the fluid fitting is configured to be mechanically attached to the fluid element by:arranging the attachment portion of the coupling body within the sleeve passageway of the bearing sleeve, such that, the coupling body and bearing sleeve assume a joined configuration,arranging the fluid element within the coupling passageway of the coupling body,arranging the joined configuration of the coupling body and bearing sleeve within the ring passageway of the drive ring, such that the coupling body axis, sleeve axis, and ring axis are substantially colinear, andaxially moving the drive ring relative to the joined configuration of the bearing sleeve and coupling body to an installed position, such that the drive ring applies a compressive force to the coupling body sufficient to cause the at least one seal of the coupling body to bite into and permanently deform the fluid element, thereby mechanically attaching the coupling body to said fluid element in a non-leaking manner.

2. The fluid fitting according to any of the preceding claims, wherein the bearing sleeve comprises polytetrafluoroethylene.

3. The fluid fitting according to any of the preceding claims, wherein the bearing sleeve is configured to conform to an outer surface of the coupling body.

4. The fluid fitting according to any of the preceding claims, wherein the bearing sleeve comprises a proximal sleeve portion, a distal sleeve portion, and an intermediate sleeve portion that connects the proximal sleeve portion and distal sleeve portion.

5. The fluid fitting according to claim 4, wherein the intermediate sleeve portion comprises a ribbed sleeve portion, the ribbed sleeve portion defining a plurality of inner ribs that are separated by inner grooves.

6. The fluid fitting according to claim 5, wherein the ribbed sleeve portion defines a plurality of outer ribs that are separated by outer grooves.

7. The fluid fitting according to claim 5 or claim 6, wherein:an outer surface of the coupling body has a ribbed surface portion that defines a plurality of outer ribs separated by outer grooves,in the joined configuration, the outer ribs of the coupling body mate with the inner grooves of the bearing sleeve, and inner ribs of the bearing sleeve mate with the outer grooves of the coupling body.

8. The fluid fitting according to claim 7, wherein:the ribbed sleeve portion defines a plurality of outer ribs that are separated by outer grooves, andin the joined configuration, the outer ribs and outer grooves of the coupling body radially align with the outer ribs and outer grooves of the bearing sleeve, respectively.

9. The fluid fitting according to any of claims 5-8, wherein the intermediate sleeve portion further comprises a cylindrical portion having an inner diameter and an outer diameter that are substantially constant along the sleeve axis.

10. The fluid fitting according to claim 9, wherein:the coupling body has a diametrically-constant surface portion having an outer diameter that is substantially constant along the coupling body axis, andin the joined configuration, the diametrically-constant surface portion of the coupling body will abut and be radially aligned with the cylindrical portion of the bearing sleeve.

11. The fluid fitting according to claim 10, wherein the inner diameter of the cylindrical portion of the bearing sleeve is substantially similar to the outer diameter of the diametrically-constant surface portion of the coupling body.

12. The fluid fitting according to any of claims 9-11, wherein the ribbed sleeve portion is distal to the cylindrical portion.

13. The fluid fitting according to any of claims 4-12, wherein the proximal sleeve portion has an inner diameter and an outer diameter that increase along the sleeve axis toward a proximal end of the bearing sleeve.

14. The fluid fitting according to claim 13, wherein:the coupling body has an upsloping surface portion having an outer diameter that increases along the coupling body axis toward a proximal end of the attachment portion, andin the joined configuration, the upsloping surface portion of the coupling body will abut and be radially aligned with the proximal sleeve portion of the bearing sleeve.

15. The fluid fitting according to claim 14, wherein:the upsloping surface portion of the coupling body extends at a first angle relative to the coupling body axis, andan inner surface of the proximal sleeve portion of the bearing sleeve extends at a second angle relative to the sleeve axis that is substantially similar to the first angle.

16. The fluid fitting according to claim 15, wherein the first angle and second angle are each from 15° to 25°.

17. The fluid fitting according to any of claims 4-16, wherein the distal sleeve portion has an inner diameter and an outer diameter that increase along the sleeve axis toward a proximal end of the bearing sleeve.

18. The fluid fitting according to claim 17, wherein:the coupling body has an upsloping surface portion having an outer diameter that increases along the coupling body axis toward a proximal end of the attachment portion, andin the joined configuration, the upsloping surface portion of the coupling body will abut and be radially aligned with the distal sleeve portion of the bearing sleeve.

19. The fluid fitting according to claim 18, wherein:the upsloping surface portion of the coupling body extends at a first angle relative to the coupling body axis, andan inner surface of the distal sleeve portion of the bearing sleeve extends at a second angle relative to the sleeve axis that is substantially similar to the first angle.

20. The fluid fitting according to claim 19, wherein the first angle and second angle are each from 15° to 25°.

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