US20070007002A1 - Washpipe seal - Google Patents

Abstract

A controlled leakage seal assembly having a first stationary portion adapted to be connected in substantially fluid-tight relation to a source of drilling fluid and a second portion adapted to be connected in substantially fluid-tight relation to a rotary portion including a washpipe. The seal includes a first housing and a stack of radially inwardly extending, spaced apart annular stators, and a second seal housing and stack of spaced apart radially outwardly extending annular rotors. The stators and rotors are interleaved with one another and axially spaced apart by a working clearance. The stators and said rotors combine to define an elongated radially and axially extending tortuous path. The seal assembly permits the washpipe and the first and second housings to rotate relative to each other in substantially fluid-tight relation except for the drilling fluid passing along the tortuous path between the rotors and stators and allows the drilling fluid to enter an outlet region at greatly reduced pressure.

Description

BACKGROUND OF THE INVENTION
• The present invention relates generally to so-called washpipe seals and more particularly, to a washpipe seal which is adapted to permit controlled leakage of a small portion of high pressure drilling fluid which largely passes into the so-called washpipe and into the drill string which is attached thereto. In the oil field industry particularly, a so-called swivel assembly incorporates a seal at the washpipe to confine the major portion of the drilling fluid to the washpipe. This drilling fluid is sometimes colloquially referred to as “drilling mud” or simply “mud.”
• In the drilling system, there are high pressure abrasive fluids which are sent down to the bore hole through the washpipe and the drill string, and ultimately to the drill motor which is held at the bottom of the drill string. This abrasive fluid is supplied to the motor which drives the cutting tools under very high pressure, e.g. 5,000 PSI to 7,500 PSI or even 10,000 PSI or more. A seal is necessary between the non-rotary upper connection assembly and the rotary lower connection assembly to prevent undue leakage of this drilling fluid to the outside. As a rule, the drilling fluid leakage is taken from the vicinity of the washpipe back to a remote container where it is again picked up and supplied to the drill string. The joint in question is between the upper connection assembly, which includes a housing for the stator assembly and the lower connection assembly which includes the rotor assembly and which is affixed to and rotates with the drill string.
• According to one embodiment of the invention, the leakage of the drilling fluid, which is operated from 5,000 PSI up to perhaps 10,000 PSI or more for example, is led through a labyrinth between alternating rotor/stator discs, which preferably include lands and grooves in each rotor/stator disc. As the flow moves along between each rotor/stator it moves a radial distance about equal to the radial extent of each stator and rotor and an axial distance approximately equal to the thickness of each rotor and stator unit.
• As a consequence of passing through this labyrinth of discs, the drilling fluid in one embodiment gradually is subject to a reduced pressure and ultimately achieves a low pressure and passes to an outlet, where it is led via a conduit back to the source of drilling fluid. Here, the drilling fluid passes back into the washpipe and undergoes a repetition of the cycle. According to the invention, only a very small portion of the drilling fluid escapes through the labyrinth seal compared to the portion of drilling fluid directed down the drill string, and the seal of the invention may thus be considered a controlled leakage seal.
• In another embodiment, the force of the controlled leakage drilling fluid is opposed by grease within the labyrinth, whereby the grease fills most or all of the labyrinth and is present at what, in another embodiment, would be the inlet for the drilling fluid. The grease thus passes backwardly through the labyrinth of rotors and stators up to the approximate point of entry of the drilling fluid. In this embodiment, the drilling fluid is sealed at the top rather than at the bottom of the labyrinth, and the grease extends back and totally fills the labyrinth defined by the rotors and stators.
• One of the features of the present invention is that the stator discs and the rotor discs are interleaved and arranged with very small clearance spaces between them. Consequently, in the stator unit there are a plurality of spacers, with a stator disc between each set of spacers. Also, there are a plurality of rotors, each one in turn separated by spacers. Consequently, there is an alternating stack of interleaved rotors and spacers which maintain the desired clearance. Each disc, in one embodiment, has a plurality of grooves of perhaps 0.030 to 0.050 inches, as well as a large plurality of lands which extend into the grooves, perhaps 0.010 to 0.040 inches by way of example. Each of the stator spacers and the rotor spacers is preferably held snugly in the desired configuration of a stack by Belleville washers or other similar units, and each of the spacer includes an O-ring or similar packing to ensure the correct alignment and spacing and to insure that there is no leakage through a secondary route.
• At the top of one embodiment of the novel rotor/stator assembly of the invention, is an annular space between sections of the housing and above the labyrinth. The drilling fluid pressure at this point is perhaps 5,000 to 10,000 PSI, but by reason of passing through the extended labyrinth with perhaps 16 to 20 reversals of radial direction and 16 to 20 axial movements as the drilling fluid moves along a tortuous path, the pressure confining the axial fluid gradually lowers until the fluid reaches the outlet, where it is under relatively low pressure and relatively low flow.
• In one preferred embodiment, there is a flow meter in series relation with the drilling fluid escaping from the outlet. In this way, if there is an unexpected or sudden increase in flow, indicative of failure, steps may be taken to promptly rectify any malfunction.
• In one embodiment of the prior art, there have been a series of seals, each seeing the highest pressure, and these seals would then fail, one at a time, until there remained only the final seal. This solution was not satisfactory, especially because of a projected seal life of only 50 to 300 hours. The present invention overcomes the difficulties with such seal designs by allowing the pressure to gradually bleed off rather than completely fail in a series of steps, each of which would see all of the pressure.
• Because the fluid to be sealed is highly abrasive, the washpipe and the housing are preferably made from an oil field grade of steel and the rotor and stator its associated parts are made from tungsten carbide or other wear-resistant alloys, which are also used to provide radial and thrust bearings where the washpipe meets the upper housing. Such parts could also be made from ceramics or other like material. These bushings or bearings are greased through one or more fittings and grease passages which are provided for that purpose.
• A known type of seal or packing is used between the lowermost portion of the washpipe and the stator and rotor housings, but this seal or packing sees only the reduced or lowermost pressure which is sensed at the outlet for the drilling fluid and accordingly, such seal is not exposed to high pressure in use.
• It is therefore an object of the present invention to provide a new and improved seal for washpipes and similar applications, in oil fields and elsewhere.
• A further object of the invention is to provide a washpipe seal wherein the high pressure drilling fluid moves gradually from a region of very high pressure, to a low outlet pressure from where it preferably is returned to the storage point for reuse.
• Another object is to provide a seal which includes a housing for a plurality of stators and a housing for a plurality of rotors, with the stators and rotors being of annular disc form and being interleaved with one another.
• A still further object of the invention is to provide a plurality of stators and rotors having interleaved portions and wherein each stator and rotor preferably includes a plurality of lands and grooves or other formations to retard the flow of drilling fluid as it works it way from the inlet chamber of the seal assembly to the outlet at the bottom portion thereof.
• A still further object of the invention is to provide a plurality of alternating rotors and stators of annular form in which each includes a seal or packing that prevents leakage between the two sets of stators and rotors.
• Another object of the invention is to provide a seal with a housing having a lower end member disposed in opposed relation to another housing member, the two being separated by thrust bearings and/or radial bearings each able to be greased, and maintaining such respective housings in closely spaced apart relation.
• A further object is to provide a plurality of stators and rotors, each of which is held in place by a spacer, with the array of spacers being held in fixed position under a compressive load provided by spring means such as Belleville washers, for example.
• Another object of the invention is to provide radially inner and outer housings, each having a plurality of associated discs, with the inner housing including disks of annular form and defining a cylindrical region on the interior, able to accommodate a high volume of drilling fluid, while passing a small amount of drilling fluid to the annular headspace or chamber between the two housings.
• A still further object of the invention is to provide a seal with controlled leakage, which includes an upper connection assembly and a housing attached thereto as well as a lower connection assembly that rotates with the washpipe in the use of the seal assembly.
SUMMARY OF THE INVENTION
• These and other objects and advantages of the present invention are achieved in practice by creating an outer housing with plural annular discs, an inner housing of annular form and having plural discs, with drilling fluid passing both inside and outside of the inner housing, with a small proportion of the drilling fluid passing through the inner housing being directed through a labyrinth of discs until it reaches the outlet.
• The manner in which these objects and advantages are achieved will become more clearly apparent when considered in conjunction with a description of the preferred embodiments of the invention and shown in the accompanying drawings in which like reference numbers indicate corresponding parts throughout.
BRIEF DESCRIPTION OF THE DRAWINGS
• FIG. 1 is a perspective view showing several important features of the present invention including showing the upper connection assembly, the lower connection assembly and the arrangement of the annular stator and rotor discs in interleaved relation;
• FIG. 2 is an enlarged vertical sectional view through a portion of the apparatus of the present invention and showing one particular preferred arrangement of the stator housing, the rotor housing, plural annular rotors and stators for each housing and other features of the invention;
• FIG. 3 is an exploded view of one annular stator and one annular rotor and showing them in spaced apart relation;
• FIG. 4 is a further enlarged vertical sectional view of a portion of the stator/rotor assembly showing the stators and rotors with lands and grooves therein, and including the spacers between the rotor and stators and the seals therefor, and showing the tortuous path undergone by the drilling fluid.
• FIG. 5 is a view similar toFIG. 4, only showing the stators and rotors without the lands and grooves.
DESCRIPTION OF THE PREFERRED EMBODIMENTS OF THE INVENTION
• While the invention may be embodied in a number of different forms, and may employ variations of certain parts, two preferred embodiments of the invention will be described, which include plural rotors and stators that are interleaved with each other and arranged in inner and outer annular housings, and which accommodate a pressure drop from up to 10,000 or more PSI to a much lower level adjacent the outlet.
• Referring now to the drawings in greater detail, there is shown washpipe seal assembly generally designated18, and this assembly, as best shown inFIGS. 2-4, includes a stator assembly generally designated20, and a rotor assembly generally designated22. Thestator assembly20 includes a plurality of discs generally designated24a,24breceived within a housing generally designated26. Thishousing26 is affixed to an upper connection assembly generally designated30. Thisassembly30 includes a radially outer member with an O-ring32 on itstop surface34. The inner member is preferably in the form of acollar36 of reduced diameter relative to thehousing26.
• An O-ring seal37 is provided on thecollar36 to seal a joint between theupper connecter assembly30 and thecollar36. A certain amount of axial freedom of movement or play may take place between theupper connection assembly30 and thecollar36 on thehousing26. The stator housing generally designated26 consists of the upper, reduceddiameter collar36, an O-ring groove38 and aradial flange46 leading to the outer diametercylindrical portion35. Adjacent the bottom of thestator housing26 is a low pressureannular chamber49 terminating in anoutlet50.
• An enlarged diameter portion generally designated52 forming a lower continuation of thehousing26 is provided, and this element includes one ormore grease fittings54 connected tosuitable passages56 for grease to lubricate radial and thrust bearing assemblies generally designated58,60. Thesebearings58,60 are subject to harsh environmental conditions and are preferably made from a hardened steel material, or tungsten carbide, and thebearings58,60 permit rotation between thestator assembly20 and therotor assembly22. Referring again to the spaced apartstators24a,24b, etc., in this embodiment, there is provided anupper spacer unit62awhich is fixed relative to thehousing26 by aBelleville washer66 capable of exerting a strong axial compressive force on the entire stack ofspacers62a,62b, etc. andstators64a,64b, etc.
• The general arrangement ofstacked stators64a,64b, etc. and the arrangement ofspacers62a,62b,62c, etc. is the same arrangement as the arrangement of rotors and spacers in therotor assembly22. Thus, thewashpipe70 has aradial flange72 which engages aBelleville washer74. This Belleville washer develops an axial load onspacers76a,76b, etc. and thesespacers76a,76bengage the margin portions of therotor discs78a,78b, etc.
• The lower connection assembly generally designated71, includes anaxial wall73, aradial wall75, and agroove77 accommodating an O-ring79. Theradial bearing58 is engaged by anextension81 of thewashpipe70. These portions may be affixed to a rotary member generally designated80 and having radial andaxial flanges82,84. These components may include their own O-rings86,88 as is customary in the industry.
• Referring again to thewashpipe70 and thehousing assembly26, the rotation between theseparts70,26 (and others fixed respectively with respect to those parts) also requires aseal90, and this seal or packing90 engages opposedinner wall portions92,94, of thewashpipe70 and thestator35. This form of “V-packing”90, however, is unlike prior art seals in that it does not see a large pressure drop and consequently it is able to endure for an extended period of time, in keeping with the life of the remainder of the seal afforded by the rotors and stators.
• Referring now to the operation of the controlled leakage seal of the invention and in particular toFIG. 4, an enlarged partial sectional view of the stators, rotors and spacers is shown. Here, spacers62a,62b, etc. hold thestators64a,64bin a relatively fixed position and allow therotors78a,78bto rotate without radial or axial engagement of theircounterparts64a,64b, etc. There is aheadspace region96 provided between theradial flanges72,46 of the twohousings26,70. Thespacers62a,62b, etc. are retained in place with the aid of the gaskets or O-rings98a,98b,98c, etc. and thespacers76a,76bare held in position with the aid of O-rings orgaskets100a,100b, etc.
• In operation, theheadspace region96 is filled with extremely high pressure drilling fluid, and this drilling fluid is then passed through thepassage105 between theend face portion102 of thespacer76aand theend face portion104 of thestator64a. It will be noted that each of thestators64a,64b, etc. has a plurality of lands orteeth106a,106b, etc. disposed in offset relation to thelands108a,108b, etc. on therotor78a.Grooves110a,110bare disposed in an opposed relation to thelands108a,108b, etc.
• With the verysmall space105 between the end faces102,104 being duplicated all along the axial and radial path between thestators64a,64b, therotors78a,78b, etc., a tortuous path of leakage is provided for the drilling fluid as it makes its way to theannular chamber49. This scheme of extremely narrow passages, both axial and radial, when repeated from 16 to 20 times, has the effect of gradually lowering the pressure from the 7,000 to 10,000 PSI to a greatly reduced pressure which will appear in thelower chamber49. From there, the drilling fluid optionally passes through aflow meter116, and from there to aconduit118 wherefrom it may be returned to the supply of drilling fluid for reuse.
• Referring now toFIG. 5 and another embodiment of the invention, an alternate construction of the rotor and stator disks is shown. In this embodiment, the stator consists of a reduceddiameter collar136, aradial flange146, and a cylindricalaxial flange135. Disposed inside thiscylindrical shell135 is aspacer162a, sealed by an o-ring198a. Severaladditional spacers162b,162c, etc. are stacked inside thiscylindrical shell135, and theadditional spacers162b,162ceach include additional O-rings198band198c. Thehead space196 lying between theradial flange172 of the inner cylinder orwashpipe170, and theradial flange146 of thecylindrical shell135 provides apassage173 for drilling fluid entering thehead space196.
• A compressive force is maintained by Belleville washer166 acting on thespacer162aand all of the components in axial alignment therewith. ABelleville washer174 bears on theinner spacer176a,176band on thedisks178a,178bentrapped between them. O-rings200a,200bseal thespaces176a,176b, etc. The only difference in operation between embodiment ofFIG. 4 and that ofFIG. 5 is that of the configuration of the rotors/stators of the invention.
• For example, theend face202 of thespacer176aand theend face204 of the stator designated164alie in opposed relation with asmall clearance205, such as 0.015 to 0.060 inches, by way of example, between them. Thehorizontal space215 between thestator164aand therotor178ais defined by the top and bottom faces212,214 of thestator164aand therotor178a. The drilling fluid passes in thespace215 between thesenarrow faces202,204 and into thespace217 between surfaces between thesurfaces218,220, and so on until the drilling fluid has reached the bottom of thechamber49 at the lower end of thewashpipe170.
• Consequently, theregion196 is filled with extremely highly pressurized drilling fluid, most of which travels down inside thewashpipe170. However, a small amount of this drilling fluid is forced into to thepassage215,217, etc. between the end portions and surface portions of the rotors and stators.
• Referring now to the stators the rotors and the means for keeping them apart, the spacers shown in the drawings are the preferred method of doing this. However it is not the only method of keeping these stators or rotors apart, since this can be done by merely forming an extension of enlarged width on the end of each rotor or stator, thereby imparting an L shape to the inboard and outboard of the stators or rotors. The O-rings such as the O-rings198a,198b, the200a,200b, etc. may be replaced with any suitable kind of packing, preferably a so-called block V or the like.
• The Belleville washer is shown as being compact and having a high spring rate which is desirable in most cases. However, a wave-type spring or washer could be used or other means having a strong spring rate to hold these elements together.
• The invention has been described showing of lands and grooves facing each other in one embodiment, and a plain ungrooved embodiment as another choice. However, it is possible to have one face grooved or the like or to have lands in the other side could be merely a planar surface. The preferred method are the tongue and groove, or lands and grooves, method illustrated or the plain, unadorned faces. Regarding the size of this space, it has been found that the most effective space depends upon the viscosity and pressure of the drilling mud, but having the lands and grooves with 0.020 to 0.050 is preferred. Some other values may be used if desired. The packing90 has been illustrated as the most economical and effective method of creating a seal between the relatively low pressures involved at the bottom of the chamber. Needless to say, however, another type of seal could be used in this application.
• Another entirely different method could use the apparatus of the present invention with no change or with only a slight change in the apparatus. In this case, the spaces between the rotors and the stators could be filled with grease up to approaching, or even meeting, theheadspace96. In this instance, the grease would have to be injected into the apparatus while there were no countervailing high pressure from the drilling mud. Once this space was filled entirely with grease, the seal would otherwise, function as designed, with the drilling and pressure being contracted with the resistance to movement of the grease.
• Preferably, the two housings, the stators and the rotors and other parts are made from tungsten carbide or similar material, since these components see the highest pressure drilling fluid. Other components use an oil field grade steel. The O-rings and the block V or similar type seals are made from synthetic rubber or other known material.
• It will thus be seen that the present invention provides a novel controlled leakage seal assembly having a number of advantages and characteristics, including those herein pointed out and others which are inherent in the invention.

Claims (13)

1. A seal assembly for controlling leakage of drilling fluid between a first stationary portion adapted to be connected in substantially fluid-tight relation to a source of drilling fluid and a second portion adapted to be connected in substantially fluid-tight relation to a rotary portion including a washpipe and a drill string, said first seal portion including a first housing and a stack of radially inwardly extending, spaced apart annular stators and a second seal portion including a second housing and stack of spaced apart radially outwardly extending annular rotors, said stators and said rotors being interleaved with one another and being axially spaced apart from one another by a working clearance, said stators and said rotors combining to define an elongated radially and axially extending tortuous path from an inlet region at one axial end of said stack of stators and rotors for receiving drilling fluid confined at high pressure and directing said fluid along said tortuous path to an outlet region at the other axial end of said stack of stators and rotors, said seal assembly permitting said washpipe and said first and second housings to rotate relative to each other in substantially fluid-tight relation except for said drilling fluid passing along said tortuous path between said stacks of rotors and stators, and allowing said drilling fluid to enter said outlet region at greatly reduced pressure.

2. A seal assembly as defined inclaim 1, wherein each of said stators and each of said rotors includes a large plurality of radially closely spaced apart, circumferentially extending lands and grooves.

3. A seal assembly as defined inclaim 1 wherein said stators and said rotors having working faces that are spaced apart by a working clearance of from about 0.010 to about 0.090 inches.

4. A seal assembly as defined inclaim 1 wherein said stators and said rotors are held in a said interleaved position by spacers lying between the radially outer margins of said stators and lying between the inner margins of said rotors.

5. A seal assembly as defined inclaim 4 wherein said spacers are confined by means for exerting a compressive force thereon.

6. A seal assembly as defined inclaim 5 wherein said means for exerting a compressive force includes Belleville washers.

7. A said assembly as defined inclaim 1 wherein said outlet region for receiving said drilling fluid at said greatly reduced pressure is an annular chamber.

8. A seal assembly as defined inclaim 1 wherein said seal assembly further includes means at said outlet region for directing said drilling fluid toward a return path, and a flow meter disposed in said return path.

9. A seal assembly as defined inclaim 7 which further includes a flow meter disposed downstream of said annular chamber.

10. A seal assembly as defined inclaim 1 wherein at least one group of said rotors and stators includes radially extending axially directed working faces having plural land and groove formations thereon to further retard the radial flow of drilling fluid through said seal assembly.

11. A seal assembly as defined inclaim 4 wherein said stators and said rotors include close radial spaces between said rotors and said stators and said spacers, thereby providing a portion of said tortuous path.

12. A seal assembly for controlling leakage of drilling fluid between a first stationary portion connected in substantially fluid-tight relation to a source of drilling fluid and a second portion connected in substantially fluid-tight relation to a rotary portion including a washpipe and a drill string, said first seal portion including a first metal housing and a stack of radially inwardly extending, spaced apart annular stators in the form of thin disks, and a second seal portion including a second metal housing and stack of spaced apart, radially outwardly extending annular rotors in the form of thin disks, said stators and said rotors being interleaved with one another and being axially and radially spaced apart from one another by a working clearance of from about 0.010 inches to about 0.090 inches, the faces and end portions of said stators and said rotors combining to define an elongated, radially and axially extending tortuous path from an inlet region at one axial end of said stack of stators and rotors for receiving drilling fluid confined at high pressure and directing said fluid along said tortuous path to an outlet region at the other axial end of said stack of stators and rotors, said seal assembly permitting said washpipe and said first and second metal housings to rotate relative to each other in substantially fluid-tight relation except for said drilling fluid passing along said tortuous path between said stacks of rotors and stators, and allowing said drilling fluid to enter said outlet region at greatly reduced pressure.

13. A seal assembly as defined inclaim 11 wherein at least one group of said rotors and stators includes radially extending axially facing surfaces having plural land and groove formations thereon to retard the flow of drilling fluid through said seal.

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