1. Field of the Invention
This invention relates generally to seals that are suitable for containing a pressurized fluid that may be abrasive, and for providing a film of lubricant at the dynamic sealing interface in response to relative rotation to enhance pressure and rotary speed capabilities.
The seals of the present invention are particularly suitable for use in rotary swivel assemblies, such as the general type of oilfield washpipe assemblies that are described in U.S. Pat. No. 2,764,428 entitled “Wash Pipe Mounting For Swivels,” IADC/SPE Paper 59107 “A New Hydrodynamic Washpipe Sealing System Extends Performance Envelope and Provides Economic Benefit,” and commonly assigned U.S. Pat. No. 6,007,105 entitled “Swivel Seal Assembly.”
2. Description of the Related Art
Rotary seals are used to establish sealing between relatively rotatable machine components, for the purpose of retaining a pressurized fluid. The type of sealing ring that is most commonly used in oilfield washpipe assemblies is typically referred to as washpipe packing, and dates at least to U.S. Pat. No. 2,394,800 entitled “Rotary Swivel.” Such conventional washpipe packing is used to retain pressurized drilling fluid. Differential pressure energizes the dynamic sealing lip against the washpipe. While this type of packing has served the oilfield for many years, it is not suitable for the higher speeds and pressures of today's deep wells. The problems and extreme expenses associated with failures of conventional packing in deep wells are described in IADC/SPE Paper 59107.
The antecedents to the packings used in many other types of applications are shown, for example, in U.S. Pat. No. 2,442,687 entitled “Packing For Stuffing Boxes” and U.S. Pat. No. 2,459,472 entitled “Rotary Swivel.”
In general, the term “packing” simply refers to a sealing ring that is intended to be used in a “stuffing box” of one sort or another. “Packing” and “stuffing box” are terms that date back to the 1770's, and perhaps earlier. A stuffing box is a housing with a deep cylindrical cavity that receives a plurality of packing rings. Some or all of the packing rings are often installed in abutting relation with spacer rings that perform a packing ring supporting function. For several examples of spacer/support rings, see the aforementioned U.S. Pat. Nos. 2,394,800, 2,442,687, and 2,459,472, and IADC/SPE Paper 59107.
Commonly assigned U.S. Pat. No. 6,334,619, entitled “Hydrodynamic Sealing Assembly,” shows a hydrodynamically lubricated packing ring assembly that has the disadvantage of requiring an expensive wavy backup ring.
Kalsi Engineering manufactures various configurations of hydrodynamic rotary seals, and sells them under the registered trademark “KALSI SEALS.” The factors involved in using such seals to contain a pressurized fluid are described in U.S. Pat. No. 6,334,619. Typical seal configurations require a lubricant pressure that is greater than, or nearly equal to, that of the contained fluid. To contain a highly pressurized fluid, one can use a pair of oppositely-facing seals; one to serve as a partition between the lubricant and the pressurized fluid, and the other to retain the lubricant, as described in conjunction with
Many applications, such as the oilfield drilling swivel, the progressive cavity artificial lift pump, centrifugal pumps, and rotary mining equipment, would benefit significantly from a hydrodynamically lubricated rotary packing ring seal having the ability to operate under conditions where pressure of the contained fluid is higher than the lubricant pressure.
The present invention is a rotary sealing arrangement that overcomes the above-described shortcomings of the prior art. The rotary seal rings of the present invention are used to establish sealing with respect to a relatively rotatable surface (such as a shaft or washpipe). A dynamic lip deforms against the relatively rotatable surface, establishing an interfacial contact footprint that varies in width from place to place.
An aspect of the present invention is to provide a simple and compact rotary sealing arrangement for containing a pressurized media such as oilfield drilling fluid, where the rotary seals employ the advantage of maintaining a film of lubricant at the dynamic sealing interface during rotary operation, without requiring the undesirable complexity of a wavy backup ring, and without the undesirable complexity of maintaining the lubricant at a pressure that is greater than the pressure of the pressurized media. Hydrodynamic geometry on a dynamic sealing lip interacts with a lubricating media during relative rotation to wedge a lubricating film into the dynamic sealing interface between the seal and the relatively rotatable surface. The lubricating film is distributed across the dynamic sealing interface and migrates toward, and into, the pressurized fluid, and thus provides a contaminant flushing action. The lubricating film reduces seal running torque, providing reduced wear and reduced seal-generated heat. In other words, the dynamic sealing lip slips or hydroplanes on a film of lubricating fluid during periods of relative rotation between the dynamic sealing lip and relatively rotatable surface. When relative rotation stops, the hydroplaning activity stops, and a static sealing relationship is re-established between dynamic sealing lip and relatively rotatable surface.
One feature of the present invention is a hydrodynamic inlet that is supported by one or more adjacent boundaries, such as a recess support corner, a first recess end and/or a support shoulder, in order to resist differential pressure-induced inlet collapse, so as to retain the hydrodynamic wedging function of the hydrodynamic inlet despite the high differential pressure acting across the rotary seal.
The dynamic sealing surface is preferably interrupted by angled slots/recesses that have a shelf-like shape on at least one side thereof. The slots/recesses incorporate a hydrodynamic inlet shape having an end that may be approximately tangent with the dynamic sealing surface.
The shelf-like shape or shapes prevent the slots/recesses from collapsing completely against the shaft when the pressure of the contained fluid is higher than that of the seal lubricant. The lubricant is swept into the dynamic interface between the dynamic sealing surface and the washpipe, at the location near the extrusion gap where it is needed most for interfacial lubrication. A shelf-like shape also creates an angled zone of locally increased interfacial contact pressure that diverts lubricant film toward the environment-side edge of the dynamic sealing surface.
A feature of a preferred embodiment of the present invention is compatibility with the type of conventional packing ring support structure that is found in conventional stuffing boxes, including, but not limited to, the washpipe assemblies that are used in oil and gas well drilling.
An optional feature of the present invention is the compression of a portion of a static sealing rim between a first sealing housing component and a second sealing housing component to establish a static sealed relationship between the first and second sealing housing components, and to prevent rotation of the seal/packing relative to the first and second seal housing components.
It is intended that the seal of the present invention may incorporate one or more seal materials without departing from the spirit or scope of the invention, and may be composed of any suitable sealing material, including elastomeric or rubber-like materials that may, if desired, be combined with various plastic materials such as reinforced polytetrafluoroethylene (“PTFE”) based plastic. If desired, the rotary seals may be of monolithic integral, one piece construction or may also incorporate different materials bonded, co-vulcanized, or otherwise joined together to form a composite structure. For use as an oilfield washpipe packing, a preferred seal material is a fabric reinforced elastomer compound.
So that the manner in which the above recited features, advantages, and objects of the present invention are attained and can be understood in detail, a more particular description of the invention, briefly summarized above, may be had by reference to the embodiments thereof that are illustrated in the appended drawings. It is to be noted, however, that the appended drawings only illustrate preferred embodiments of this invention, and are therefore not to be considered limiting of its scope, for the invention may admit to other equally effective embodiments that vary only in specific detail.
In the drawings:
The rotary seal of a preferred embodiment of the present invention is illustrated generally at 2 in its installed condition, in the absence of differential pressure in
With reference to
The terms “ring-like” and “ring” are used with the understanding that the term “ring” is commonly understood to encompass shapes other than perfectly circular. As an example, a decorative finger ring often has beaded edges or a sculpted shape, yet is still called a ring. As another example, the “ring” of U.S. Pat. No. 1,462,205 is not everywhere circular. There are thousands of precedents for using the term “ring-like” in a patent, and many patents use the term in conjunction with a seal or a body of a seal. For example, see U.S. Pat. Nos. 612,890, 4,361,332, 4,494,759, 4,610,319, 4,660,839, 4,909,520, 5,029,879, 5,230,520, 5,584,271, 5,678,829, 5,833,245, 5,873,576, 6,109,618, and 6,120,036. Note that in many of the examples, the seal in question has features that result in the shape not being everywhere circular. For example, in some cases the dynamic lip of the ring-like seal has a wavy lubricant-side shape.
The rotary seal 2, being a generally circular ring, defines a theoretical axis. While the theoretical axis is not illustrated, the term “axis” is well-understood in the art, and in the field of drafting is sometimes illustrated using a centerline. For orientation purposes, it should be understood that in all of the cross-sectional views herein, the cutting plane of the cross-section is aligned with and passes through the theoretical axis of the rotary seal 2; i.e., the theoretical centerline lies on the cutting plane. The circumferential direction of relative rotation is normal (perpendicular) to the plane of the cross-section, and the theoretical centerline of rotary seal 2 generally coincides with the axis of relative rotation.
Referring to
In the preferred embodiment of the present invention, the dynamic sealing lip 4 and the static sealing rim 6 are integral features of the rotary seal 2. The dynamic sealing lip 4 is adapted for sealing against a relatively rotatable surface 8 of a first machine component 10 as shown in
The rotary seal 2 is installed within a seal groove that is typically defined by a first groove wall 12, a second groove wall 14, and a peripheral wall 16. The seal groove and the relatively rotatable surface 8 together form what is commonly called a seal gland. The peripheral wall 16 is positioned in spaced relation to the relatively rotatable surface 8. Seal gland arrangements are possible where the second groove wall 14 is unnecessary. When the second groove wall 14 is used, it is positioned in spaced relation to the first groove wall 12.
The seal groove is preferably defined by a second machine component 18 that may be formed of one or more components. In
If desired, the first spacer ring 20 and a second spacer ring 22 can be generally shaped like the conventional spacer rings that are shown in the conventional washpipe assembly of
The first spacer ring 20 and the second spacer ring 22 may be retained or attached together by any suitable retaining or attachment means, including, for example, threaded means such as threads, bolts, screws, studs, hammer unions, etc., and including external clamping means, bayonet-type latches, deformable rims or tangs, retaining ring(s), welding, soldering, bonding, friction, interference fit, etc., without departing from the spirit or scope of the invention. The first and second spacer rings 20 and 22 may be made from any suitable material, such as, for example, metal, plastic or reinforced plastic, or a combination thereof.
The most common method for securing the first spacer ring 20 and the second spacer ring 22 together is to axially clamp them inside of a housing, as shown, for example, in U.S. Pat. No. 2,394,800 and
Although the second machine component 18 is illustrated as an assembly formed by two separable components, such is not intended to limit the scope of the invention. The manner of positioning the rotary seal 2 admits to other equally suitable forms. For example, the rotary seal 2 could be configured for installation within a groove that is formed in a second machine component 18 that is of one piece construction.
On a washpipe, the relatively rotatable surface 8 is an external cylindrical shape. Although the invention is disclosed here in the context of a familiar washpipe packing-type of seal, such is not intended to limit the configuration of the relatively rotatable surface 8. It is well-established that hydrodynamic rotary seals can be configured for, and used in, both radial- and face-sealing applications.
Relatively rotatable surface 8 can take the form of an externally- or internally-oriented, substantially cylindrical surface, as desired, with rotary seal 2 positioned radially between peripheral wall 16 and relatively rotatable surface 8, in which case the axis of relative rotation would be substantially parallel to relatively rotatable surface 8. In a radial sealing configuration, dynamic sealing lip 4 is oriented for compression in a substantially radial direction, and peripheral wall 16 may, if desired, be of substantially cylindrical configuration.
Alternatively, relatively rotatable surface 8 can take the form of a substantially planar surface, with rotary seal 2 compressed axially between peripheral wall 16 and relatively rotatable surface 8 in a “face-sealing” arrangement, in which case the axis of relative rotation would be substantially perpendicular to relatively rotatable surface 8. In an axial (face) sealing configuration, dynamic sealing lip 4 is oriented for compression in a substantially axial direction, and peripheral wall 16 may be of substantially planar configuration. In what is contemplated to become the most common configuration, relatively rotatable surface 8 is the external cylindrical surface of a shaft, sleeve, or washpipe.
In summary, the rotary seal 2 can be configured for uses as a radial seal or a face seal by configuring the dynamic sealing lip 4 to be located at either the inside diameter, the outside diameter, or the end of the seal, while maintaining the advantages of the invention that are disclosed herein.
The static sealing rim 6 is adapted for sealing with respect to the second machine component 18. Typically, the static sealing rim 6 is adapted for sealing with respect to the second machine component 18 by virtue of being adapted to establish sealing contact pressure with respect to the second machine component 18. This sealing contact pressure is typically achieved by having some part of the static sealing rim 6 in compressed contact with the second machine component 18. However it is achieved, when the rotary seal 2 is installed, the static sealing rim 6 establishes a sealed relationship with the second machine component 18. In the example shown in
The dynamic sealing lip 4 incorporates a dynamic sealing surface 26 for sealing contact with the relatively rotatable surface 8. In the uncompressed state of the rotary seal 2 (
The rotary seal 2 may be composed of any suitable sealing material, including, for example, elastomeric or rubber-like materials such as an elastomer compound or a combination of one or more elastomer compounds, various plastic materials, different materials bonded together to form a composite structure or inter-fitted together, or a combination of a suitable plastic and an elastomer compound. It is preferred, however, that the seal 2 be made from a reinforced material, such as fabric-reinforced elastomer compound.
For use in oilfield washpipe assemblies, the rotary seal 2 is typically made primarily from a fabric-reinforced elastomer compound. Commonly used materials include cotton fabric-reinforced nitrile rubber (NBR), cotton fabric-reinforced hydrogenated nitrile rubber (HNBR), and aramid fabric-reinforced HNBR. As is commonly done with oilfield washpipe packings, a local end portion of the static sealing rim 6 may be constructed of a ring of homogeneous elastomer compound (for example, see
It is commonly understood by those of ordinary skill in the art that elastomers used in seal construction are compounds that include one or more base elastomers. Such base elastomers include, but are not limited to, HNBR (hydrogenated nitrile rubber), HSN (highly saturated nitrile), FKM (fluorocarbon rubber), FEPM (also known as TFE/P or tetrafluoroethylene and propylene copolymer), and EPDM (ethylene propylene diene monomer). Such compounds may include other compounding agents including fillers, processing aids, anti-degradants, vulcanizing agents, accelerators, and activators. The effects of the ingredients used are generally understood by those of ordinary skill in the art of compounding elastomers. Likewise, the ingredients used in manufacturing plastics that are used in seal construction are generally understood by those of ordinary skill in the art of developing plastic seal materials.
A low pressure end 30 of the rotary seal 2 has a surface that generally faces the first groove wall 12, and is adapted for being in supporting contact therewith. As shown in
When the low pressure end 30 and the first groove wall 12 have mating “V” shapes, the first groove wall 12 comprises first wall part 12A and first wall part 12B, and the low pressure end 30 comprises low pressure end portion 30A and low pressure end portion 30B as shown in
The first groove wall 12 forms a support surface for the rotary seal 2. As shown, it is preferable that at least a portion of the first groove wall 12 (i.e., first wall part 12B) establishes a tapered (i.e., shaped like a portion of a cone) support surface for the rotary seal 2. Preferably, any remaining portion of the first groove wall 12 establishes the first wall part 12A. A part of the first groove wall 12 is preferably angulated, establishing an acute included angle 62 with respect to the relatively rotatable surface 8 of the first machine component 10.
The rotary seal 2 is designed for relative rotation with respect to the relatively rotatable surface 8. It is to be understood that this relative rotation can be achieved by rotating the first machine component 10, or by rotating the rotary seal 2, or by simultaneously rotating both the rotary seal 2 and the first machine component 10 independently. If the rotary seal 2 is to be rotated, it is preferred that it be accomplished by rotating the second machine component 18. Referring to
The rotary seal 2 preferably has an exclusion edge 32 that is preferably generally circular, in accordance with the teachings of the prior art. When the rotary seal 2 is installed, the exclusion edge 32 contacts the relatively rotatable surface 8 as shown in
Since perfect theoretical circularity is seldom if ever obtainable in any feature of any manufactured product in practice, it is to be understood that when “circular,” “substantially circular,” “substantial circularity,” or similar terms are used to describe attributes of the invention, the terms are not to be misconstrued as an intent to achieve the unobtainable; i.e., perfect theoretical circularity.
As illustrated in
The rotary seal 2 is used to retain the contained media 40, which is from time to time maintained at an elevated pressure. For the purposes of this specification, the term “contained media” encompasses any media that the rotary seal 2 may be required to retain, such as, but not limited to, drilling fluid, other types of fluid, dirt, crushed rock, manure, dust, lubricating media, a process media, seawater, air, sand, metallic projectiles, plastic pellets, etc. For purposes of this specification, the term “fluid” has its broadest meaning, encompassing both liquids and gases.
In an oilfield washpipe assembly, the contained media 40 is drilling fluid, which is also known as drilling mud. The contained media 40 is typically communicated to the rotary seal 2 by a media passage 41 that is typically established by clearance between the first machine component 10 and the second machine component 18 as shown in
Still referring to
The extrusion gap bore 43 may, if desired, establish a journal bearing relationship with the relatively rotatable surface 8, and that journal bearing relationship may be used to guide the relatively rotatable surface 8 relative to the second machine component 18, or vice-versa.
The lubricant 44 is preferably fed into the lubricant passage 42 from some type of lubricant supply. Various types of lubricant supply systems are known in the art. For example, see the various types of lubricant supply systems that are shown and/or described in the publicly available Kalsi Seals Handbook, Revision 1 and the lubricant supplies shown in various U.S. Patents, such as, for example, U.S. Pat. Nos. 5,195,754, 5,279,365, 6,007,105, and 6,227,547.
The purposes of the rotary seal 2 of the preferred embodiment are to establish sealing engagement with the relatively rotatable surface 8 of the first machine component 10 and with the second machine component 18, to retain the contained media 40, and to cause a film of the lubricant 44 to migrate toward and preferably into the contained media 40 for lubrication of the rotary seal 2 and the relatively rotatable surface 8, and for flushing purposes.
When the pressure of the contained media 40 is greater than the pressure of the lubricant 44 as illustrated in
When the pressure of the contained media 40 is greater than the pressure of the lubricant 44, the resulting differential pressure also deforms the rotary seal 2 in a way that causes all or substantially all of the low pressure end 30 of the rotary seal 2 to be in contact with the first groove wall 12. Thus, the rotary seal 2 is supported against the pressure of the contained media 40 by the first groove wall 12, as taught by U.S. Pat. No. 2,394,800. Within the seal industry, the first groove wall 12 is sometimes referred to as the “lubricant-side wall,” and the second groove wall 14 is sometimes referred to as the “environment-side wall.”
The dynamic sealing lip 4 has at least one recess 48 of the general type disclosed in more detail below in conjunction with
The recess 48 comprises a hydrodynamic ramp 50 and a recess flank 52. The recess flank 52 is preferably adjacent to the hydrodynamic ramp 50, as shown. The recess flank 52 preferably forms a ledge, as shown in
A principal aspect of the recess 48 is that it is exposed to and contains some of the lubricant 44, and thereby allows at least a part of the hydrodynamic ramp 50 to be exposed to the lubricant 44. One purpose of the recess flank 52 is to support the recess 48 against total collapse when the pressure of the contained media 40 is greater than the pressure of the lubricant 44 (
Referring to
The recess 48 preferably interrupts (i.e., cuts into) both the dynamic sealing surface 26 and the low pressure end 30. The dynamic sealing surface 26 varies locally in its width along its circumference as a result of the recess 48. Preferably, at least part of the recess flank 52 is skewed relative to the direction of relative rotation 46. For example, and as disclosed above, as the recess flank 52 traverses the dynamic sealing surface 26 circumferentially, it may taper from a position adjacent the low pressure end 30 toward the exclusion edge 32, as shown in
The first recess end 54 preferably forms a closed end, as shown. The closed end is preferred because it supports the recess 48 against collapse when differential pressure is acting on the rotary seal 2 in its installed state, thereby preserving lubricant communication to the hydrodynamic ramp 50. Because the first recess end 54 preferably forms a closed end, the recess 48 ends abruptly, rather than passing on through and forming the alternate first recess end 54A that is represented by a dashed line in
At least one support shoulder 57 is incorporated along or near the side of the recess 48 that is oriented toward the exclusion edge 32. The support shoulder 57 is preferably relatively abrupt near the first recess end 54, and preferably merges smoothly into the dynamic sealing surface 26 at or near the second recess end 56. If desired, the support shoulder 57 can, as shown, form the transition between the recess flank 52 and the dynamic sealing surface 26.
As shown in
As measured relative to the dynamic sealing surface 26, the recess 48 preferably has maximum depth at or near the first recess end 54, as shown in
As previously described, the dynamic sealing surface 26 has a maximum surface width 34 and a minimum surface width 36. The minimum surface width 36 is equal to the maximum surface width 34 minus the maximum recess width 58.
In the absence of differential pressure, some of the area of the dynamic sealing surface 26 near the exclusion edge 32 contacts the relatively rotatable surface of the first machine component, establishing an interfacial contact footprint of some width (as shown, for example, in
When the force produced by high differential pressure acts on the at least one force receiving surface 28, additional area of the dynamic sealing surface 26 is deformed into contact with the relatively rotatable surface 8, causing more of the dynamic sealing surface 26 to contact the relatively rotatable surface 8; i.e., the footprint spreads. Typically, at some high enough magnitude of differential pressure, all or nearly all of the dynamic sealing surface 26 is deformed into contact with the relatively rotatable surface 8. It is possible that even a small portion of the low pressure end 30 near the lubricant end transition 60 might also be brought into contact with the relatively rotatable surface 8 when the rotary seal 2 is exposed to severe differential pressure.
If desired, the maximum recess width 58 can be sized such that no portion of the hydrodynamic ramp 50 at the second recess end 56 engages the relatively rotatable surface 8 of the first machine component 10 in the absence of differential pressure. That is, the hydrodynamic ramp 50 would only begin to engage the relatively rotatable surface 8 of the first machine component 10 and perform a hydrodynamic wedging function when some level of differential pressure is applied across the rotary seal 2. When so designed, the hydrodynamic ramp 50 does not serve any hydrodynamic wedging function until the differential pressure applied across the rotary seal 2 is sufficient to cause a portion of the hydrodynamic ramp 50 to contact the relatively rotatable surface 8 of the first machine component 10. When so designed, the hydrodynamic wedging action provided by the hydrodynamic ramp 50 provides a progressively stronger hydrodynamic wedging action as the differential pressure increases and brings more of the dynamic sealing surface 26 and more of the width of the hydrodynamic ramp 50 into contact with the relatively rotatable surface 8 of the first machine component 10. In other words, the hydrodynamic ramp 50 can be configured to provide more hydrodynamic interfacial lubrication when more lubrication is needed due to the higher differential pressure.
Alternately, if desired, the maximum recess width 58 can be designed so that at least a portion of the hydrodynamic ramp 50 at the second recess end 56 already engages the relatively rotatable surface 8 of the first machine component 10 at the time of installation, even in the absence of differential pressure. When so designed, the hydrodynamic ramp 50 serves a hydrodynamic wedging function even in the absence of differential pressure, whenever relative rotation occurs.
One purpose of the support shoulder 57 is to support the recess 48 when differential pressure acting across the seal 2 forces additional area of the dynamic sealing surface 26 against the relatively rotatable surface 8 of the first machine component 10. The reason for providing such support is so that at least a portion of the recess 48 remains out of contact with the rotatable surface 8 of the first machine component 10. It is desirable that at least a portion of the recess 48 remains “open” (not in contact with the relatively rotatable surface 8), and can thereby provide lubricant communication to the location where the hydrodynamic ramp 50 contacts the relatively rotatable surface 8 of the first machine component 10.
The location where the hydrodynamic ramp 50 contacts the relatively rotatable surface 8 of the first machine component 10 forms a hydrodynamic inlet. When the relatively rotatable surface 8 rotates in the direction of relative rotation 46 with respect to the rotary seal 2 as shown in
The hydroplaning activity that occurs during relative rotation minimizes or prevents the typical dry rubbing wear and high friction associated with conventional non-hydrodynamic packing elements, prolonging the useful life of the rotary seal 2 and the life of the mating relatively rotatable surface 8 of the first machine component 10, and making higher speed, and differential pressure, practical.
As described previously, when the above-described relative rotation is occurring, the interfacial contact footprint becomes a dynamic interface, also known as a “dynamic sealing interface.” During relative rotation, a net hydrodynamic pumping related leakage of the lubricant 44 preferably occurs as lubricant 44 is transferred across the dynamic sealing interface and into the contained media 40.
When all or nearly all of the dynamic sealing surface 26 is in contact with the relatively rotatable surface 8 of the first machine component 10, the portion of the rotary seal 2 that experiences the most stress is at or near the lubricant end transition 60, which is the transition between the dynamic sealing surface 26 and the low pressure end 30. The lubricant end transition 60 often takes the form of a corner, as shown, and if desired, this corner may be slightly rounded, as shown. The material near the lubricant end transition 60 experiences conditions that in the prior art cause significant wear. The hydrodynamic ramp 50, being circumferentially in line with the dynamic interface near the lubricant end transition 60, feeds lubricant 44 directly into that critical location. This causes that critical location (and the rotary seal 2 as a whole) to run much cooler than prior art packing. This cooler operation increases the extrusion resistance of the rotary seal 2 at the critical location near the lubricant end transition 60 by increasing the modulus of elasticity of the rotary seal 2 near the lubricant end transition 60 (and near the lubricant passage 42 of
Along at least part of the location where the support shoulder 57 contacts the relatively rotatable surface 8 of the first machine component 10, a zone of elevated interfacial contact pressure occurs within the interfacial contact footprint. Preferably, at least part of this zone of interfacial contact pressure is skewed with respect to the direction of relative rotation 46, and therefore during relative rotation, the zone of interfacial contact pressure diverts part of the film of lubricant 44 toward and past the exclusion edge 32, and into the contained media 40. The skewed zone of interfacial contact pressure created by the support shoulder 57 serves to flush contaminant matter from the dynamic interface, and thereby helps to minimize wear of the dynamic sealing surface 26.
Referring now to
The pressure of the contained media 40 also imposes force on the at least one force receiving surface 28, which causes the contact footprint width to increase; i.e., the footprint spreads. It also causes the sealing contact pressure between the dynamic sealing surface 26 and the relatively rotatable surface 8 to increase. Because of the recess 48, the contact footprint width 38 is smaller at some locations than others. In
The recess flank 52 serves to prop at least part of the recess 48 open, so that not all of the hydrodynamic ramp 50 is in contact with the relatively rotatable surface 8, and so that at least some portion of the recess 48 remains “open” (i.e., not in contact with the relatively rotatable surface 8). The recess support corner 49 also preferably helps to keep the recess 48 open. The first recess end 54 (
To reiterate, if part of the left-hand side of the recess 48 is collapsed against the relatively rotatable surface 8, the open part of the recess 48 is still exposed to the extrusion gap bore 43 and the lubricant 44 and the open part of the recess 48 can serve as an open passage (i.e., a communication path) for supplying the lubricant 44 to the hydrodynamic inlet that is formed by the hydrodynamic ramp 50 converging generally circumferentially into contact with the relatively rotatable surface 8. Since the inlet consumes lubricant 44 and pumps a film of lubricant 44 toward and past the exclusion edge 32, it is critical that at least part of the recess 48 be propped open and can thereby perform its intended lubricant passageway function. Some features of this invention, such as the recess flank 52, the recess support corner 49, and the first recess end 54, their proximity to each other, and the shape of the recess 48, cooperate together with the first and second machine components 10 and 18 to allow the recess 48 to remain open despite the actions of high differential pressure, and to perform its intended functions.
With regard to
Because the pressure of the contained media 40 is greater than the pressure of the lubricant 44, the contained media 40 produces a force on the force receiving surface 28 that causes the interfacial contact pressure near the recess flank 52 to be locally elevated. Since at least part of the recess flank 52 is preferably skewed relative to the direction of relative rotation between the relatively rotatable surface 8 and the dynamic sealing lip 4, at least part of the elevated zone of interfacial contact pressure near the recess flank 52 is also preferably skewed relative to the direction of relative rotation 46, thereby encouraging the lubricant film within the sealing interface to migrate toward and past the exclusion edge 32 in response to relative rotation between the relatively rotatable surface 8 and the dynamic sealing lip 4. The direction of relative rotation 46 is normal to the plane of the cross-section; in other words it is normal to the
A principal advantage of the preferred embodiment of the present invention is that the recess flank 52, the recess support corner 49, (and, if desired, the wall-like configuration of the first recess end 54 illustrated in
Referring now to
In the embodiment of
The static sealing rim 6 is adapted for sealing with respect to the second machine component 18 by establishing sealing contact pressure with respect to the second machine component 18 achieved by having the static sealing rim 6 in compressed contacting relationship with the second machine component 18. The compressed contacting relationship is established by axial clamping of the static sealing rim 6 between the first spacer ring 20 and the second spacer ring 22 of the second machine component 18.
The dynamic sealing lip 4 incorporates a dynamic sealing surface 26 for sealing contact with the relatively rotatable surface 8, includes at least one force receiving surface 28, and preferably has an exclusion edge 32 that is generally circular.
The low pressure end 30 of the rotary seal 2 generally faces, and is supported against differential pressure, by the first groove wall 12. The first groove wall 12 preferably comprises first wall part 12A and first wall part 12B, and the low pressure end 30 of the rotary seal 2 preferably comprises low pressure end portion 30A and low pressure end portion 30B.
When installed, a portion of the dynamic sealing surface 26 contacts the first machine component 10, thereby establishing a contact footprint width 38 therewith.
Referring now to
In the description of the seal of the embodiment shown in
If desired, the second material 66 need not extend to the end transition 68 between the low pressure end portion 30A and the low pressure end portion 30B, thus making it easier for the pressure of the contained media 40 to force the surface of the second material 66 into contact with the relatively rotatable surface 8 (without flattening the recess 48 against the relatively rotatable surface 8). As described previously, a lower modulus portion 70 of the static sealing rim 6 can be incorporated if desired, as is commonly done with washpipe packings.
The energizer element 72 can take any of a number of suitable forms known in the art including, but not limited to, elastomeric rings and various forms of springs, without departing from the scope or spirit of the invention. If desired, the energizer element 72 can be located by an annular recess of any suitable form, and preferably at least part of the annular recess is defined by a force receiving surface 28. Differential pressure acting on the energizer element 72 applies force to the annular recess, including the portion of the force receiving surface 28 that is contacted by the energizer element 72.
The advantage of using such a prior art hydrodynamic seal 74 in conjunction with the rotary seal 2 of the present invention is that the pressure of the lubricant 44 can be maintained at a value that is greater than that of a low pressure environment 76. Although the low pressure environment 76 can be any type of environment, in an oil well drilling washpipe assembly the low pressure environment 76 is typically the atmosphere, and the objective of the assembly is to prevent escape of the contained media 40 into the low pressure environment 76. If desired, the lubricant 44 can be supplied via a lubricant port 78. In other words, the rotary seal 2 of the present invention can be used in the pressure staged manner first taught in the commonly assigned U.S. Pat. No. 6,007,105 entitled “Swivel Seal Assembly,” which teaches that the rotary seals of that pressure-staged invention may take any suitable form, such as hydrodynamic-type or chevron-type seals, and also discloses that the rotary seals may conveniently take the form of hydrodynamic seals such as those patented and sold by Kalsi Engineering, Inc. or any one of a number of rotary shaft seals that are suitable for the purposes intended, such as reinforced elastomeric chevron-type seals that are conventionally used in many swivels.
If desired, the lubricant 44 may be supplied through the lubricant port 78 by any suitable lubricant supply system 80, such as, but not limited to, those described in commonly assigned U.S. Pat. Nos. 6,007,105 and 6,227,547, and/or those shown in the Kalsi Seals Handbook, Revision 1. If desired, the lubricant supply system 80 can be protected against contamination (i.e., contamination due to exposure to the contained media 40 in the event of failure of the rotary seal 2) by using a check valve 82. Thermal expansion of the lubricant 44 is not an issue, because the dynamic sealing lip 4 of the rotary seal 2 will lift and vent any significant lubricant pressure into the contained media 40.
As shown, if desired, the first spacer ring 20 may form a housing that extends over the second spacer ring 22. A unique feature of
The outboard seal is the rotary seal 2 of the present invention. The overall objective of the assembly is to partition a contained media 40 from a lubricant 44A within the assembly, where the pressure of the contained media 40 can occasionally be much greater than the pressure of the lubricant 44A, but for the most part the pressure of the lubricant 44A is slightly greater than (or alternately, about equal to) that of the contained media 40. In a downhole drilling tool, the contained media 40 is drilling fluid (i.e., “drilling mud”), and the lubricant 44A is typically used by the drilling tool for various purposes, such as lubricating bearings, operating hydraulic motors and hydraulic cylinders, etc. It is necessary to contain the contained media 40 so that it does not enter the drilling tool and contaminate the inner workings of the tool.
In this particular type of assembly, the lubricant 44 would typically be called a barrier lubricant, and the outboard seal, the rotary seal 2, would typically be called a “barrier seal.” This “barrier seal” nomenclature is an understatement as it concerns the present invention because the rotary seal 2 fulfills much more than the traditional barrier seal function.
If desired, the initial fill of the lubricant 44 may be supplied through a lubricant port 78. If desired, the lubricant port 78 may be connected to any suitable lubricant supply system 80 while the assembly is in service, or alternately the lubricant port 78 can be plugged while the assembly is in service.
The prior art hydrodynamic seal 74 retains a volume of the lubricant 44A and its hydrodynamic pumping-related leakage enters the lubricant 44 through the lubricant passage 42. Since the pressure of the lubricant 44A is typically greater than that of the contained media 40, the prior art hydrodynamic seal 74 is used to contain the lubricant 44A, in view of the fact that the rotary seal 2 of the present invention cannot handle differential pressure acting from that direction. Also, circumstances are possible where the pressure of the lubricant 44A may temporarily be significantly higher than that of the contained media 40, and the prior art hydrodynamic seal 74 is configured to deal with such circumstances.
When the pressure of the contained media 40 is temporarily significantly greater than that of the lubricant 44, the rotary seal 2 deforms in the manner described in conjunction with previous figures herein, so that it can operate in a hydrodynamic interfacial lubrication regime.
The prior art hydrodynamic seal 74 is not well suited to service where the pressure of the contained media 40 is significantly greater than that of the lubricant, and the rotary seal 2 is not well suited to service where the pressure of the lubricant is greater than that of the contained media 40. By pairing the two types of seals in the manner illustrated in
It can be appreciated that the various constructions of rotary seal 2 that are illustrated herein can be used in the assemblies of
If desired, the novel recess 48 described in conjunction with the various embodiments of the present invention may be configured for combination with the basic prior art seal cross-sectional shapes that are shown in U.S. Pat. No. 6,334,619, in order to eliminate the wavy seal lubricant end and wavy backup ring that are described in U.S. Pat. No. 6,334,619.
In view of the foregoing it is evident that the present invention is one that is well adapted to attain all of the features hereinabove set forth, together with other objects and features which are inherent in the apparatus disclosed herein. Even though several specific hydrodynamic rotary seal and seal gland geometries are disclosed in detail herein, many other geometrical variations employing the basic principles and teachings of this invention are possible.
The foregoing disclosure and description of the invention are illustrative and explanatory thereof, and various changes in the size, shape, and materials, as well as in the details of the construction shown and described, may be made without departing from the spirit of the invention. The present embodiments are, therefore, to be considered as merely illustrative and not restrictive, the scope of the invention being indicated by the claims rather than the foregoing description, and all changes which come within the meaning and range of equivalence of the claims are therefore intended to be embraced therein.
This application claims the benefit of U.S. Provisional Patent Appln. No. 61/268,698 filed Jun. 15, 2009, entitled “Hydrodynamic Washpipe Packing Ring.” U.S. Provisional Patent Appln. No. 61/268,698 is hereby incorporated by reference herein.
Number | Date | Country | |
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61268698 | Jun 2009 | US |