WO2002077499A1 - Dispositif d'etancheite rotatif - Google Patents

Dispositif d'etancheite rotatif Download PDF

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Publication number
WO2002077499A1
WO2002077499A1 PCT/US2001/009048 US0109048W WO02077499A1 WO 2002077499 A1 WO2002077499 A1 WO 2002077499A1 US 0109048 W US0109048 W US 0109048W WO 02077499 A1 WO02077499 A1 WO 02077499A1
Authority
WO
WIPO (PCT)
Prior art keywords
lubricant
pressure
rotary
housing
chamber
Prior art date
Application number
PCT/US2001/009048
Other languages
English (en)
Inventor
Manmohan S. Kalsi
Lannie L. Dietle
Gunther Heidt
William T. Conroy
Jeffrey D. Gobeli
John E. Schroeder
Original Assignee
Kalsi Engineering, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kalsi Engineering, Inc. filed Critical Kalsi Engineering, Inc.
Priority to US10/296,327 priority Critical patent/US20030205864A1/en
Priority to PCT/US2001/009048 priority patent/WO2002077499A1/fr
Priority to CA002409174A priority patent/CA2409174A1/fr
Publication of WO2002077499A1 publication Critical patent/WO2002077499A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/18—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings
    • F16J15/182—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings with lubricating, cooling or draining means
    • F16J15/183—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings with lubricating, cooling or draining means using a lantern ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/162—Special parts or details relating to lubrication or cooling of the sealing itself
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/324—Arrangements for lubrication or cooling of the sealing itself

Definitions

  • the present invention relates generally to rotary sealing devices for hydrodynamically
  • hydrodynamic sealing between relatively rotatable members, such as between a
  • hydrodynamic seal or seals serve as one or more
  • invention concerns a contaminant pressure responsive, lubricant pressure amplified rotary rod seal
  • invention concerns a rod seal cartridge for progressing cavity artificial lift pumps or injection pumps
  • the progressing cavity artificial lift pump is relatively simple in principle concept
  • top drive a compact surface mounted rotary drive head unit
  • the pump stator is attached to the lower
  • the rotor is attached to the lower end of a rod string typically consisting of conventional lift pump sucker rods.
  • the rod string and rotor are supported and rotationally driven
  • injection pumps for pumping high pressure fluids into wells.
  • the surface mounted drive unit is mounted to the well head, and provides a flow tee to direct
  • the drive unit also incorporates a sealed and lubricated
  • bearing housing assembly containing rotary bearings which axially and radially support a
  • the spindle/shaft which in turn supports the rod string.
  • the spindle is rotationally driven by a prime mover such as an electric or hydraulic motor.
  • the bearing housing and stuffing box are usually
  • the stuffing box which also provides the space needed to temporarily clamp-off the rod string
  • the yoke is sometimes called a "booth" within the top drive industry.
  • drive unit also incorporates coupling means to rotationally drive the rod string.
  • coupling means to rotationally drive the rod string.
  • the bearing guided rotary spindle of the bearing housing is hollow and incorporates a
  • the stuffing box has been the conventional stuffing box arrangement provided to seal-off the relatively rotating rod string as it enters the yoke area.
  • the stuffing box is filled with conventional packing, which is a far
  • the leakage contains abrasives which accelerate packing wear, and cause
  • polish rod specially prepared rod called a “polished rod” or “polish rod” is provided.
  • the polished rod is
  • the surface of the polished rod quickly becomes damaged from handling and environmental exposure
  • Misalignment between the bearing housing and the stuffing box can also be a
  • seal cartridge may be external of the seal cartridge or incorporated within the structure of the seal cartridge, which
  • piston or pistons function as a pressure transferring wall of a lubricant chamber and are acted upon
  • contaminant pressure also referred to as pump pressure
  • An objective of the present invention is to provide a rotary seal cartridge for progressing
  • Another feature of the present invention is a bearing guided sleeve which rotates in unison
  • the clamping arrangement also makes the outer races immune
  • the lubricant pressure amplified rotary seal cartridge has a housing member having a passage therethrough and having at least a portion of
  • a rotary member such as a cartridge wear
  • sleeve is disposed for rotation within said passage and is supported for rotation by a bearing assembly, such as one or more rotary cone bearings which accommodate both side loads and axial
  • a plurality of spaced seals establish sealing
  • lubricant chambers between the housing and the rotary member. At least one and preferably
  • two or more cylinders are provided, each having a lubricant supply chamber which is in fluid
  • a piston is moveable within each of the
  • a second surface area being different from the first surface area and being exposed to contaminant
  • contaminant pressure is employed to define contaminant pressure
  • Contaminant pressure may be gas pressure from a well
  • ambient pressure or “environment pressure” is defined as the pressure of the environment in which the seal cartridge mechanism is located.
  • the contaminant pressure acts on the second surface area and develops a lubricant pressure within the lubricant supply chamber which is different from contaminant pressure.
  • the contaminant pressure acts on the second surface area and develops a lubricant pressure within the lubricant supply chamber which is different from contaminant pressure.
  • lubricant pressure is amplified above contaminant pressure so that the lubricant pressure within each
  • seals are preferably hydrodynamic seals, the higher lubricant pressure acts to enhance the wedging
  • the cylinder and piston assemblies may be arranged to develop pressure staging
  • Lubricant pressure may be staged by appropriate arrangement of the
  • lubricant chamber which is higher than contaminant pressure and by achieving lubricant
  • FIG. 1 is a sectional view of a contaminant pressure responsive, lubricant pressure amplified
  • FIG. 2 is a partial sectional view of an alternative embodiment of the present invention
  • FIG. 3 is a partial sectional view of another of another alternative embodiment of the present
  • FIG.4 is a sectional view of a contaminant pressure responsive, lubricant pressure amplified rotary rod seal cartridge representing a further alternative embodiment of the present invention
  • the cartridge can be retrofit to existing top drive units by the use of adapters;
  • FIG. 5 is a sectional view of a contaminant pressure responsive, lubricant pressure amplified rotary rod seal cartridge representing a further alternative embodiment of the present invention
  • FIG. 6 is a sectional view of a contaminant pressure responsive, lubricant pressure amplified
  • FIG. 7 is a sectional view of a contaminant pressure responsive, lubricant pressure amplified
  • rotary rod seal cartridge representing a further alternative embodiment of the present invention and showing a rotary wear sleeve being secured in non-rotational relation with a rotary driven polished
  • FIG. 7A is a partial sectional view of a rod seal cartridge representing a further alternative
  • FIG. 8 is a sectional view of a contaminant pressure responsive, lubricant pressure amplified
  • FIG. 9 is a sectional view of a contaminant pressure responsive, lubricant pressure amplified rotary rod seal cartridge representing another alternative embodiment of the present invention.
  • FIG. 10 is a sectional view of an alternative embodiment of the present invention showing
  • seal cartridge housing having seals for sealing between the housing and a polished rod
  • FIG. 11 is a sectional view similar to that of FIG. 10 and showing separation of the lubricant
  • FIG. 12 is a fragmentary sectional illustration showing a housing having seals for sealing
  • FIG. 13 is a sectional view of a contaminant pressure responsive, lubricant pressure
  • driven rotary shaft penetrates a vessel, reservoir, or other structure and is in contact with or contains
  • FIG. 1 a contaminant pressure responsive
  • lubricant pressure amplified rotary rod seal cartridge such as is employed for rotary well pumps
  • the rotary rod seal cartridge 10 is shown generally at 10.
  • cartridge mounting base 16 and the mounting flange 18 may vary widely in
  • the bearing and seal housing 12 defines an internal bearing locator shoulder 20 which
  • bearing assembly have respective rolling bearing engagement with tapered roller bearing elements
  • the wear sleeve is supported for rotation and guided during rotation by the wear sleeve bearing assembly and defines a central passage 37 within which is received a polished
  • the rod with respect to another structure.
  • the rod is "polished" because it is prepared by finishing
  • bearing cone 28 is supported and located by a support ring 38 which is in turn supported by a retainer
  • seal carrier housing 12 is disposed in sealing engagement with an annular external cylindrical surface
  • bearing and seal retainer 48 defines an internal bore 58 which forms a part of a centrally located
  • the wear sleeve 36 defines a smooth, wear resistant outer sealing surface 60 which is engaged by an annular hydrodynamic sealing element 62 carried within an internally facing annular
  • the annular seal 62 is
  • annular bearing lubricant chamber or reservoir 66 which is defined between the
  • the wear sleeve 36 defines an outer coating 68 also composed of an
  • abrasive resistant material such as nickel based tungsten carbide or any one of a number of other
  • annular sealing elements 72 and 74 are hydrodynamic seals embodying
  • the lowermost one of the spaced sealing elements 72 and 74 is oriented with its axially
  • groove 76 which is an internal groove of the bearing and seal retainer housing 12 located between
  • the bearing and seal retainer housing 12 defines at least one and preferably a plurality of lubricant supply passages 78 which are disposed in
  • the lubricant supply groove 80 is in fluid communication with a lubricant supply
  • the cylinder 84 and is in fluid communication with the lubricant chamber 82 thereof via a lubricant
  • the cylinder 84 is fixed to the bearing and seal retainer housing 12 by retainer bolts
  • an obround seal 90 such as an O-ring which
  • a piston 92 is moveable within the cylinder 84 and is sealed with respect to an internal cylindrical surface 94 of the cylinder by an annular high pressure seal 96.
  • a piston stem 98 extends
  • a compression spring 108 is positioned about the piston stem with its lower end located against the
  • retainer 112 which is secured to the piston stem by a retainer ring 114 that is received by an external retainer groove of the piston stem.
  • the piston 92 defines a contaminant pressure responsive area 116 which is of greater dimension than a lubricant pressure responsive area 118, and to which contaminant pressure, which
  • contaminant may also be referred to as pump pressure or well pressure, is communicated by a contaminant
  • the contaminant passage 120 is sealed
  • sealing element 125 which is oriented about the passage 120 and disposed in sealing engagement
  • any of the hydrodynamic seals will be in a direction from a lubricant chamber toward the
  • the plug member 113 is provided with a tapered upper surface 123 which minimizes the
  • the tapered upper surface 123 also serves as a means for determining the volume of contaminant fluid which may enter the cylinder.
  • the bearing and seal retainer housing 12 defines at least one lubricant supply passage 124 which is in
  • a lubricant supply passage 130 defined generally at the
  • cylinder 136 chamber establishes lubricant supply communication with an internal lubricant supply
  • a lubricant fitting 137 is fixed to the cylinder 136 and is in communication with the internal lubricant supply chamber 138 via a lubricant fill passage 139.
  • amplification cylinder is also secured to the bearing and seal retainer housing 12 by retainer bolts
  • a piston member 140 is moveable within the cylinder 136 and incorporates a high pressure sealing element 142 for maintaining dynamic sealing
  • stem 148 which may be integral with the piston 140, extends through an opening 150 in the top wall
  • a compression spring 156 is positioned about the piston stem 148 with its lower end in engagement with the upper wall 134 of the cylinder. The upper end of the
  • compression spring 156 bears against a spring retainer 160 which is secured to the piston stem by
  • This ratio may be changed by changing the dimension of the
  • the lower end of the cylinder 136 is closed by a plug member 164 which is sealed to the
  • annular sealing member 168 which is retained within
  • annular retainer ring 170 located within an internal retainer groove at the bottom of the
  • contaminant laden pumped fluid may enter the cylinder via a contaminant pressure supply passage
  • the plug member 164 is provided with a tapered upper surface 174 which minimizes the volume
  • the tapered upper surface 174 also provides for
  • bearing and seal retainer housing 12 defines a mounting flange 176
  • member 178 is secured to the mounting flange 176 by bolts 180 or by
  • the yoke 178 provides support for a bearing housing
  • housing 12 is integrated into the top drive assembly and serves as a necessary structural
  • the wear sleeve 46 defines a drive flange 186 having drive receptacles that
  • a seal retainer 185 retains the seals 183
  • the wear sleeve During rotation of the wear sleeve, the wear sleeve is supported and stabilized with respect to the
  • a bushing 192 which may be composed of
  • the bushing 192 provides the additional function of providing
  • polished rod serves to exclude entry of large dimensioned particulate and minimizes entry of
  • the piston stems 98 and 148 each define lubricant pressure relief recesses 241 and 242
  • the lubricant supply chambers of the respective cylinders 84 and 136 are filled via lubricant fittings
  • Piston position, and cylinder pressure can also be compared to ascertain seal chamber integrity.
  • Piston position, and cylinder pressure can also be compared to ascertain seal chamber integrity.
  • FIG.2 defines a lower housing end 14 having an integral mounting flange 194 having a circle of
  • a seal member 204 is employed for sealing between the mounting
  • 194 and 200 may also be provided with sealing surfaces for metal to metal sealing as well as or in
  • housing element 12 defines a lower end 14 having a circle of internally threaded bolt
  • openings 210 at the lower mounting end 212 for mounting of the housing to a suitable support flange, adapter or other supporting structure, not shown.
  • a suitable support flange, adapter or other supporting structure not shown.
  • a sealing element 213 is employed to establish sealing of the lower end
  • housing structure is not required to function additionally as a structural member for support of a drive head support yoke as in FIG. 1.
  • the support flange or other support structure in this case would be any suitable support structure.
  • the housing to be manufactured at significantly less cost as compared to the embodiment of FIG. 1,
  • a common mounting base 211 is provided to provide support for the cartridge
  • the mounting base 211 has a central opening 215 through which the polished rod 190 extends and defines an internally threaded mounting receptacle 214 having a circular sealing
  • the common mounting base 210 also serves as a common mounting base 210 to connect to the common mounting base 211.
  • the contaminant fluid pressure within the well bore or pumped fluid passage 122 is the contaminant fluid pressure within the well bore or pumped fluid passage 122.
  • pressure communicating passages 120 and 172 also communicate with cylinder receptacles 218 and 220 which form portions of the contaminant fluid pressure receiving cylinder chambers of the
  • Mounting bolts 222 extend through openings in the mounting
  • An annular seal element 224 establishes sealing at the interface of the lower end of the housing
  • the cylinder 84 is mounted to the common support base 211 by mounting bolts 226 and is sealed with respect to the support base by an annular sealing
  • cylinder 136 is mounted to the base 211 by mounting bolts 230 and is sealed
  • annular sealing element 232 to the mounting base by an annular sealing element 232.
  • lubricant chamber 66 to provide for lubrication of the bearing assemblies and to provide lubricant
  • a lubricant supply conduit 234 is connected in communication with the lubricant supply passage 86 of the cylinder 84 and is also connected in
  • a lubricant supply passage 236 of the housing which generally corresponds in
  • chamber 82 of the cylinder 84 is pressurized and is conducted via the lubricant supply conduit to the
  • lubricant being communicated to the lubricant chamber 66 will be determined by the spring force of the compression spring and by the area differential defined by the contaminant pressure and
  • the cylinder 136 is communicated with the lubricant chamber 76 between the hydrodynamic seals
  • a lubricant supply conduit 238 which has one end thereof in communication with the lubricant supply passage 130 of the cylinder 136 and its opposite end in communication with a
  • lubricant supply passage 240 essentially corresponding to the lubricant supply passage 124 of FIGS.
  • the lubricant present within the lubricant supply chamber 138 is subjected to
  • the piston stems 98 and 148 each define lubricant pressure relief recesses 241 and 242
  • FIG. 6 an alternative embodiment of the present invention is shown which
  • seal cartridge mechanism is mounted to a common base structure 211 in similar manner as discussed
  • the lubricant pressure being supplied to the lubricant chamber from the lubricant supply chamber of the cylinder has a ratio of lubricant pressure with respect to contaminant pressure
  • piston stem 106 projects downwardly from the piston and through a piston opening of the common
  • This pressure staging arrangement is particularly useful in injection pumps, where the pressure
  • FIG. 7 of the drawings is a sectional view similar to that of FIG. 1, but showing the rotatable
  • seal carrier housing 246 which is adapted at its lower end with threaded bolt openings
  • the housing 246 defines a generally cylindrical internal bearing surface 58
  • a bushing 192 which may be composed of bronze or any other suitable
  • the bushing material serves to stabilize a polished rod 190 with respect to the lower portion of the housing.
  • the bushing 192 provides the additional function of providing a close clearance with the
  • Annular seals 62, 72 and 74 are located within annular internal seal grooves of the
  • the annular seals 62, 72 and 74 are hydrodynamic seals for hydrodynamically enhanced
  • the sleeve defines a stuffing box having seals such as O-ring seals 183 therein for sealing between the polished rod 190 and the wear sleeve.
  • the upper end portion 250 of the wear sleeve defines an
  • a seal retainer cap element 185 defines a top
  • FIG. 7A discloses an alternative seal retainer and collet clamp
  • 264 defines a tapered outer surface 266 which is engaged by an internally tapered surface 268.
  • clamp element 264 is driven radially inwardly by the reaction of tapered surfaces 266 and 268 for
  • An annular stop flange 270 engages the upper end of the wear sleeve and prevents over-compression of the annular sealing elements 183 as the retainer cap is further threaded to
  • the present invention is also applicable to situations where the use of a rotary sleeve is not
  • FIG. 4 Thus like components of these Figures are referred to by like reference numerals.
  • a circular sealing element 216 provides for sealing of the housing with respect to the base, adapter or other support structure.
  • the housing defines an internal bore 58 which is dimensioned for bearing or joumaled engagement
  • a plurality of annular seals 62, 72 and 74 are retained within internal seal grooves of the
  • seals 62, 72 and 74 are hydrodynamic
  • the lubricant pressure amplification or modification cylinder 84 is in communication with the housing/polished rod interface 280 via passages 86, 80 and 78 and by annular lubricant supply
  • the annular region between the seals 72 and 74 is supplied with pressurized lubricant from
  • FIG. 9 is a sectional view of a further alternative embodiment of the present invention, shown generally at 10, having an integral housing and lubricant pressure amplification system for the rotary
  • pressure amplified rotary rod seal cartridge 10 is provided with a body structure 12 having an upper
  • body structure 12 projects a pair of cylinders 84 and 136 which are preferably integral with the body
  • the cylinders 84 and 136 are arranged in diametrically opposed relation, but such
  • a piston member 92 is moveable and is sealed with respect to an internal cylindrical surface 94 of the cylinder by an annular sealing element 96.
  • piston 92 extends through a seal 104 which is carried by a removable cylinder wall 284 which is
  • the end wall 284 is sealed with respect to the cylinder by
  • annular sealing element 288 is annular sealing element 288.
  • the piston, cylinder and end wall collectively define a lubricant supply chamber 82 which
  • the piston stem 98 is supplied with lubricant via a lubricant supply fitting 87 and passage 89.
  • the piston stem 98 is supplied with lubricant via a lubricant supply fitting 87 and passage 89.
  • the lubricant venting feature is important to prevent damage to the seal cartridge mechanism in the event a
  • the thermally expanding lubricant will drive the piston in a direction toward the
  • This lubricant venting feature provides a visual indication that the cylinder is completely filled with lubricant and also minimizes the potential for damaging internal components of the cylinder or seal cartridge by over-filling and lubricant thermal expansion. For example, if seal 72 is a
  • hydrodynamic seal the hydrodynamic pumping action thereof could potentially over-fill lubricant
  • tapered or chamfered pressure relief shoulder also serves a guiding function to guide the piston stem
  • roller bearing 86 extending through a structural member 292 is in communication with the lubricant chamber 66 within which the roller bearing assemblies are contained.
  • seals 66, 72 and 74 are hydrodynamic seals so that movement of the lubricant during
  • the opposite cylinder 136 is also provided with a removable cylinder wall 294 which is
  • a retainer ring 296 secured within the end of the cylinder by a retainer ring 296 or other suitable method, such as a circle
  • supply passage 130 extends through another structural element 300 and communicates the lubricant
  • the contaminant pressure present within the pumped fluid or contaminant passage 122 acts simultaneously on the pistons 92 and 140 and thus simultaneously develops
  • housing and cylinder arrangement shown in FIG. 9 is easily manufactured by simple techniques,
  • contaminant pressure may be communicated directly to seals that establish sealing between the housing 12 and polished rod 190.
  • the removable cylinder 132 is mounted
  • the chamber or passage 172 is at pump or
  • Lubricant is communicated from the lubricant supply chamber 138 of the
  • the seals 72 may be hydrodynamic seals such as indicated above, or the seals may have any of the seals 72.
  • seals 72 are retained by a seal retainer 287
  • FIG. 11 differs from the embodiment of FIG. 10 in that the cylinder 136
  • housing 12 are in communication with a lubricant supply conduit 291 for conducting pressurized
  • a contaminant or pumped fluid supply conduit 293 is connected to the cylinder closure plug member 164 and is in communication
  • the plug member 164 defines a tapered surface
  • FIG. 12 basically discloses the housing 12, seal retainer 287 and polished rod 190 which
  • a plurality of seals 77 which may be of any suitable type such as
  • the seals are spaced, with the upper seals being subjected to
  • FIG. 13 of the drawings is a sectional view showing a contaminant pressure
  • responsive lubricated rotary rod seal cartridge generally at 10 having a housing 302 having a bottom
  • the bottom wall 304 is provided with threaded bolt holes 308 which
  • a seal 310 is received within an annular seal groove of the bottom wall 304 for
  • bottom wall 304 also defines a centrally oriented recess 312 which is in communication with a pumped fluid supply passage 314.
  • the centrally oriented recess 312 also defines a portion of a
  • the housing structure 302 also defines an interior bearing and seal support housing which
  • interior bearing and seal support housing 12 is integral with and projects upwardly from the bottom
  • the bearing assemblies have inner roller bearing cones 26
  • a rotary wear sleeve 36 is supported by the bearings within the centrally located passage 314 and is retained in relation to the bearing assemblies by support rings
  • a retainer element 48 has threaded assembly with the upper
  • annular retainer extension 46 which may be integrated with, or separable from retainer element 48.
  • annular seal 62 which may be a hydrodynamically lubricated sealing element is carried
  • the seals 62 and 72 cooperate with the housing 12 and the wear sleeve to define an annular lubricant chamber 66 and seals 72 and 74
  • housing structure defines a contaminant pressure passage 320 which is in communication with an annular piston chamber 322 having a bottom wall 324 and a pair of spaced facing cylindrical wall
  • a pair of annular piston members 330 and 332 are moveable within the
  • annular piston chamber and are urged in one axial direction by respective compression springs 108
  • annular hydrodynamic seals 62, 72 and 74 thus provides for efficient abrasive exclusion of the
  • the annular piston 330 has an annular seal 334 which is disposed in sealing engagement with the cylindrical internal surface 326 of the side wall 306 of the housing structure.
  • annular sealing element 339 With respect to the side wall by an annular sealing element 339.
  • Annular piston member 332 carries an external seal 350 which is in sealing engagement with
  • the pistons 330 and 332 regardless of the positions thereof within the annular piston chamber 322.
  • the piston 332 is also provided with an annular seal 354 which is in sealing engagement with the
  • the annular piston 332 is also shown in its
  • a cylindrical extension 360 of the annular piston 332 is in sealing
  • a lubricant supply passage 364 is drilled or otherwise formed in the wall structure of the
  • a lubricant supply port 368 in the depending annular bearing retainer 46 communicates the lubricant supply passage with the lubricant
  • seals 72 and 74, the wall structure of the housing 12, the bottom wall 304 and the side wall 306 is

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Devices (AREA)

Abstract

L'invention concerne une cartouche d'étanchéité rotative, réagissant à la pression des contaminants, de type à amplification ou modification de pression de lubrifiant (10), pour pompes de puits rotatives et autres mécanismes rotatifs. Un boîtier (12) doté d'un passage soumis à la pression des contaminants, comporte un manchon rotatif de protection contre l'usure (36) soutenu par des roulements et raccordé en étanchéité au boîtier par une pluralité de joints espacés (62, 72, 74) qui définissent au moins une (66) et de préférence deux (76) ou plus de deux chambres de lubrifiant pour assurer la lubrification des roulements et l'étanchéité hydrodynamique. Des cylindres d'amplification de pression de lubrifiant (84, 136) communiquent avec leurs chambres de lubrifiant correspondantes pour l'écoulement de fluide. Des pistons (92, 140) se déplacent dans les cylindres, définissant des surfaces différentielles exposées à la pression du lubrifiant et des contaminants. La pression des contaminants agit sur les pistons et induit une pression de lubrifiant différente, de préférence supérieure, mais pouvant être inférieure à la pression des contaminants. Lorsque la pression du lubrifiant est supérieure à la pression des contaminants, un effet directionnel est induit par rapport à la pression des contaminants ou à la pression ambiante, pour réduire au minimum le risque d'infiltration de contaminants dans les chambres de lubrifiant et pour améliorer l'effet de coinçage hydrodynamique du lubrifiant dans l'interface d'étanchéité dynamique entre les joints et l'élément rotatif, permettant ainsi de prolonger la durée de vie des joints, même sous pression élevée.
PCT/US2001/009048 2001-03-22 2001-03-22 Dispositif d'etancheite rotatif WO2002077499A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US10/296,327 US20030205864A1 (en) 2001-03-22 2001-03-22 Rotary sealing device
PCT/US2001/009048 WO2002077499A1 (fr) 2001-03-22 2001-03-22 Dispositif d'etancheite rotatif
CA002409174A CA2409174A1 (fr) 2001-03-22 2001-03-22 Dispositif d'etancheite rotatif

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2001/009048 WO2002077499A1 (fr) 2001-03-22 2001-03-22 Dispositif d'etancheite rotatif

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Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1600149A (en) * 1924-06-05 1926-09-14 Surjaninoff Michael Water-tight bearing
US2155628A (en) * 1937-11-10 1939-04-25 John C Williams Bearing seal
US2355390A (en) * 1943-03-02 1944-08-08 Murphy Daniel Bearing
US3955822A (en) * 1975-03-28 1976-05-11 Dresser Industries, Inc. Rod pump stuffing box control system
US4146237A (en) * 1977-05-31 1979-03-27 Kommanditbolaget United Stirling (Sweden) Ab & Co. Sealing device for Stirling engine piston rod in which no separation of oil and gas is necessary
US4475735A (en) * 1982-03-08 1984-10-09 Brennstoffinstitut Freiberg System for sealing shafts against solid containing gaseous media
US5305854A (en) * 1991-09-20 1994-04-26 The Texacone Company Stuffing box lubricator
US5636847A (en) * 1995-09-13 1997-06-10 Chesterton International Company Dual face seal clean barrier fluid and dynamic pressure control system
US5823541A (en) * 1996-03-12 1998-10-20 Kalsi Engineering, Inc. Rod seal cartridge for progressing cavity artificial lift pumps
US6116609A (en) * 1997-12-17 2000-09-12 A. W. Chesterton Company Fluidic feedback pressure regulation system for a mechanical seal

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1600149A (en) * 1924-06-05 1926-09-14 Surjaninoff Michael Water-tight bearing
US2155628A (en) * 1937-11-10 1939-04-25 John C Williams Bearing seal
US2355390A (en) * 1943-03-02 1944-08-08 Murphy Daniel Bearing
US3955822A (en) * 1975-03-28 1976-05-11 Dresser Industries, Inc. Rod pump stuffing box control system
US4146237A (en) * 1977-05-31 1979-03-27 Kommanditbolaget United Stirling (Sweden) Ab & Co. Sealing device for Stirling engine piston rod in which no separation of oil and gas is necessary
US4475735A (en) * 1982-03-08 1984-10-09 Brennstoffinstitut Freiberg System for sealing shafts against solid containing gaseous media
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