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WO2004092539A1 - Tete de commande de pompe amelioree comportant un presse-etoupe et un systeme de serrage integres - Google Patents

Tete de commande de pompe amelioree comportant un presse-etoupe et un systeme de serrage integres Download PDF

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Publication number
WO2004092539A1
WO2004092539A1 PCT/IT2003/000779 IT0300779W WO2004092539A1 WO 2004092539 A1 WO2004092539 A1 WO 2004092539A1 IT 0300779 W IT0300779 W IT 0300779W WO 2004092539 A1 WO2004092539 A1 WO 2004092539A1
Authority
WO
WIPO (PCT)
Prior art keywords
tube
head according
stuffing box
seals
clamp
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/IT2003/000779
Other languages
English (en)
Inventor
Mariano Pecorari
Pietro Pecorari
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SAI HYDRAULICS Inc
Original Assignee
SAI HYDRAULICS 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 SAI HYDRAULICS Inc filed Critical SAI HYDRAULICS Inc
Priority to US10/553,392 priority Critical patent/US20070051508A1/en
Priority to CA002522257A priority patent/CA2522257A1/fr
Priority to AU2003292540A priority patent/AU2003292540A1/en
Priority to MXPA05011096A priority patent/MXPA05011096A/es
Priority to BRPI0318253-3A priority patent/BR0318253A/pt
Publication of WO2004092539A1 publication Critical patent/WO2004092539A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
    • E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
    • E21B43/121—Lifting well fluids
    • E21B43/126—Adaptations of down-hole pump systems powered by drives outside the borehole, e.g. by a rotary or oscillating drive

Definitions

  • the invention relates to an improved pump drive with integrated stuffing box and clamp, i.e. a drive head for mounting at the top of a crude oil well pipe for operating the pump installed in the well, the pump being most commonly a positive displacement rotary design having a progressing helical cavity.
  • constant delivery rate wells mount electric motors connected drivingly to the pump shaft, the pump being as mentioned most commonly a rotary positive displacement type with a progressing helical cavity.
  • a hydraulic motor is provided with a variable ratio hydraulic drive for tracking the well delivery rate up to steady state.
  • the power transmission of the drive may include a gear or belt arrangement.
  • the pump is to be coupled to the drive somewhere above the stuffing box, such that the interior of the well pipe, where the oil pressure is that created by the pump or is the pressure of the well itself, can be held isolated and the drive advantageously maintained at atmospheric pressure.
  • the transmission bearing block must withstand high axial thrust forces .
  • the dual function of the drive main bearings/pump shaft thrust bearing invariably involves overhauling the whole drive, rather than just the thrust bearing as the component most subject to fail.
  • Field disassembly of the drive requires more than an hour, compared to the 20 to 40 minute time limit for the well shutdown.
  • the prior art is open to considerable improvement m the way of providing the head with a pump drive which can obviate the above deficiencies and make the servicing procedures faster to complete and more effective m a reliable manner.
  • the underlying technical problem of the invention s to provide a pump drive head, the stuffing box and/or thrust bearing of which can be readily replaced without the drive having to be disassembled in the field, and while still using the conventional checking method of tapping at different levels .
  • Another object is to allow for both standard and packing-type seals to be replaced the same way.
  • Not least an object is to provide a clamp of simple construction to effectively hold the ' rotary shaft locked during servicing operations .
  • an improved pump drive head having an integrated stuffing box and comprising: a power transmission coupled to the rotating pump driveshaft within a crude oil well, a stuffing box to retain the pressure; a thrust assembly adapted to take the tensile force exerted on said pump shaft; characterized m that said power transmission comprises a tube arranged to be rotated coaxially with the shaft and having at least two different diameters; that the rotary seals fit over the small outside diameter of the tube to establish fluid-tightness between said tube and the body of the stuffing box, the outside diameter of the seals being smaller than the large outside diameter of said tube; that the tube-to- shaft fit incorporates static seals; and that the rotating and static seals are adapted, by virtue of a retainer ring provided, to come away along with said tube and the component parts associated with the seals mside said stuffing box.
  • the tube being rotated coaxially with the shaft, is connected with its bottom end axially to a sleeve for rotation therewith and to jointly define said large and small diameters, the small diameter locating inside the stuffing box and the tube and sleeve, once connected together, forming a unitary piece .
  • a gasket is provided on the bottom end of said tube/sleeve for rotation therewith, the outside diameter of the gasket being a labyrinth pattern.
  • the rotary seals are packing seals
  • an oil seal is provided downstream of the rotary seals and of the inlet hole for the liquid lubricant to the packing; the packing being mounted between said tube/rotating sleeve and the inner seat of the stuffing box.
  • the packing is mounted on said rotating sleeve through at least one detent ring and a pre-load spring between the packing and said retainer ring.
  • the packing is mounted around the small diameter of said tube/rotating sleeve and is held there by at least one axial retainer ring and a pre-load spring placed between the packing and the axial thrust assembly.
  • the static seals are placed for reduced radial bulk in the joint region between said tube and said sleeve, and are compressed there to make a tight seal as said tube and sleeve are made fast together.
  • the static seals are placed for convenient replacement in the joint region between said tube and the shaft, and make a tight fit within the skirt of the top cover.
  • said tube is connected to the thrust assembly for rotation therewith by a rotating hub held in place by a guiding tighten-down means.
  • said hub is formed on its inside diameter with an axial slot for pulling out the connection tongue between said tube and the drive.
  • the packing pre-loading spring in the stuffing box is disposed inside a split casing to prevent overloading the spring when in the compressed state.
  • a ring spacer is provided in the stuffing box which is bored for communication with the liquid lubricant inlet hole and is formed with an annular seat for a lip- type oil seal arranged to contact the diameter of said tube/sleeve.
  • said bored ring spacer is formed with an axial middle ledge for insertion past the lip of an adjacent ring seal .
  • a gasket with a labyrinth pattern on its inside diameter is keyed to the bottom end of the sleeve for rotation therewith.
  • a shaft locking clamp advantageously placed within the body of the stuffing box, comprises a jaw pair, one pulls and one pushes, operated through a screw arranged to act with its end on one jaw and engaged in a threaded hole formed in the other jaw; said push and pull jaws being operated through a screw arranged to act with its end on the push " jaw and engaged in a threaded hole formed in the pull jaw.
  • a clamp with self-centering jaws is associated with the body of the stuffing box, the jaws gripping the shaft in a wedge contact relationship of the outer surfaces of the jaws to the inner surface of the sliding body of the clamp under the action of the tighten-down screw; advantageously, this wedge contact is achieved by provision of a conical surface taper.
  • the radial gripping movement of the self-centering jaws is guided by a prismatic fit of the clamp on the box or the cover; an elastic means is mounted between the two jaws to open them when the clamping action is released; advantageously, the shaft-gripping surfaces are semicircular about a center that is offset from the shaft centerline in a direction toward the opposite jaw.
  • Figure 1 is a longitudinal section view of the improved head according to the invention, showing the overall configurations of the stuffing box, drive (here a gear power transmission) , thrust bearing, and c].amp for locking the pump driveshaft;
  • Figure 2 is a partial enlarged view limited to the rotating bearings of the drive, thrust bearing, and stuffing box;
  • Figure 3 is a vertical cross-section view of the self- centering clamp for locking the pump driveshaft;
  • Figure 4 is a sectional plan view of the clamp of the preceding Figure;
  • Figure 5 is a longitudinal section view of the improved head, with an unspecified drive, showing the overall configurations of the stuffing box, thrust bearing, and clamp for locking the pump driveshaft;
  • Figure 6 is an enlarged detail view of the head shown in Figure 5;
  • Figure 7 is a sectional view of the stuffing box highlighting the' packing mount;
  • Figure 8 is a sectional view of another embodiment of the improved head incorporating a modification of the stuffing box and the self
  • the wellhead 1 is shown to include the drive 2 with gears 3, 4 that are driven by the motor M, the gear 4 being keyed to a rotating tube 5 connected upwardly to the thrust assembly 6 and, through the conventional coupling 7, to the rotating driveshaft 8 of the pump down the well bore.
  • the stuffing box 9 is shown beneath the drive 2 and as being advantageously integrated here to the self-centering clamp 10 with jaws for locking the shaft 8.
  • FIG. 2 shows in greater detail the main bearings 11 for the gear wheel 4 on the housing 12 of the drive 2.
  • the rotating tube 5 is keyed to the gear wheel 4 by the tongue 13 and extends coaxially within the gear wheel 4.
  • the bottom end 14 of the tube 5 is threaded at 15 for engagement with the rotating sleeve 16 of the stuffing box.
  • Static ring seals 17 are held compressed between said end 14 and the sleeve 16, these being the parts that would bear on the rings during rotation.
  • the rotating sleeve 16 of the stuffing box carries the axial thrust bearing 18 arranged, inside the body 19 of said box, to take the axial load from the well pressure acting on the seals 20.
  • the retainer ring 22 Engaged threadably with the bottom end 21 of said rotating sleeve 16 is the retainer ring 22 arranged to retain said seals and used for pulling them off, the seals being shown held apart by spacers 23 that abut against said thrust bearing 18.
  • a rubber gasket 24 is connected to the retainer ring 22 which is formed with a peripheral labyrinth pattern 25 on its outside diameter to catch as much as possible of the solids trapped in the pumped fluid.
  • a radial tapping hole 26 is formed above the gasket 24 and at each oil seal 20 for use, when required, to check the respective upstream seal for leakage under the well pressure.
  • said tube 5 is shown connected rotatably to the hub 27 of the thrust bearing, to which it is fastened together with the top cover 28 by the screws 29.
  • This hub can rotate under the bell 30 covering the bearing 31 of the thrust assembly 6, and has an upper oil seal 32.
  • This bell is fastened to the housing 12 of the drive 2 by screws 33.
  • Said hub 27 is formed with" an axial slot 34 on its inside diameter to allow the tongue 13 to be pulled away without the thrust assembly 6, i.e. the hub 27, bell 30 and bearing 31 having to be disassembled.
  • Figure 3 shows the pull and push jaws 35 and 36 around the outside diameter of the shaft 8.
  • the contact areas are knurled horizontally as at 37.
  • the jaw pair are closed by the outside-operated screw 38, which screw is provided with a seal 39 around its stem 40 to stop leakage of pressurized fluid.
  • the female threadway is formed on the body of the pull jaw 35, and the end of the screw 41 acts on the push jaw 36.
  • the clamp 10 is shown open, and is shown closed in Figure 4.
  • at least two pins 43 and two springs 44 are placed between the pull jaw 35 and the cover 42, which are effective to keep the jaws from turning and bias them to the open position.
  • Shown in Figure 5 is the head for the power transmission 45 to the shaft of the pump 8 of a crude oil well, when the head is constructed other than from gears, e.g. comprises a pulley (not shown) keyed to the tube 46 by the tongue 47 ' to rotate with the tube.
  • the thrust assembly 6 is provided with a hub 48, similar to the hub 27 described above but formed with no axial slot. This thrust assembly, having to take radial forces on said tube 46 as well, additionally includes a radial bearing 49 and the sleeve 16 of the stuffing box 9.
  • Figure 6 shows in further detail the stuffing box with the oil seals 20 and intervening rings 23, and the static seals 17 held tight on said shaft 8 by the end 14 of the tube 46.
  • the hub 48 guides the sleeve 16 of the stuffing box, and above this, said tube 46. In this it differs from the embodiment shown in Figure 2, wherein the sleeve 16 of the stuffing box and the tube 5 are guided on the hub of the gear wheel 4.
  • Figure 7 shows the bottom end 21 of said rotating sleeve 16 engaged threadably with the ring 22 to retain said packing 50, itself located between said sleeve and the inner seat 51 of the .stuffing box 9.
  • the packing is retained on said sleeve by the retainer ring 22, the detent rings 52 and spring 53 against said axial thrust bearing 18.
  • a bored ring spacer 54 and an oil seal 55 are provided between the packing 50 and said bearing 18.
  • Said inner seat 51 has a shoulder 56 for abutment by the ring 52 in the assembled state.
  • the spring 53 is to pre-load the packing 50, and in the assembled state, the ring 22 will be held spaced apart from the bottom detent ring 52.
  • the tapping holes 57 where provided, are covered by the packing 50.
  • the hole 58 is to admit lube oil to the inside diameter of the packing as this is sliding across the outer 'surface of said rotating sleeve 16.
  • the well fluid would rise above the bearing 18 and overflow through the vent hole 59 at atmospheric pressure.
  • FIG. 8 Another embodiment of the head is illustrated by Figures 8 to 11.
  • the integrated stuffing box 60 where a sleeve 61 is rotated rigidly with the shaft 8 in rubbing relationship to the packing 50.
  • This sleeve extends coaxially with and is firmly coupled in sealed relationship to the tube 62 that transfers the motion from the gear 4 to the coupling 7 via the skirt 63 of the cover 28.
  • the static seals 64 are placed between the cover skirt and the shaft 8, so that the seals 64 can be readily pulled off by first uncoupling the coupling 7 and removing the cover 28 with the skirt 63.
  • the clamp 65 is shown located beneath said integrated stuffing box with its self-centering jaws 66 closed by actuation of- just the lead screw 67 and by effect of the conical fit 68 provided between the jaws and the sliding body 69.
  • FIG. 9 Shown in Figure 9 is the body 12 of the head 1, whose upper portion 70 receives the thrust assembly 6 mounted under the bell 71, the latter being fastened by screws 72.
  • the body 73 of the stuffing box 60 is an integral part of the drive housing 12 and is formed with two radial holes, of which the lower one 74 is located upstream of the packing 50 same as the lowermost one of the holes 57, and the upper one 75 same as hole 58, for supplying clean lube oil to the rotary packing-type seal 50 acting on the outside diameter of the sleeve 61.
  • the gasket 76 with labyrinth 77, in static contact with the shaft 8, is keyed to the bottom end of the sleeve 61 for rotation therewith.
  • Said bottom end of the sleeve also carries the axial retainer ring 78 for pulling off the internal components of the stuffing box 60.
  • An axial retainer ring 79 being larger than ring 78, is mounted between the lowermost packing 50 and an axial ledge 80 on the body 73.
  • a casing split into two halves 81 and 82 that are spaced apart to enclose the packing pre-load spring 83. The casing contacts with its top portion the ring 84, which ring is drilled radially to provide a passage for the pressurized lube oil from the hole 75.
  • This middle ledge 87 is to transfer a possible axial thrust load directly to the axial thrust bearing 18.
  • an isolating ring 89 provided for the thrust bearing 31, fits over the outer diameters of the hub 27 and the hub of gear 11.
  • FIGS 10 and 11 illustrating another embodiment of the self- centering clamp 65 for locking the shaft 8, show recesses 90 provided in the body 69 for the shaft 8 to go through during the clamp-down operation.
  • Each said self-centering jaw 66 is provided with a pin 91 for guided movement in the slot 92 formed in the cover 93 of the clamp casing 94.
  • Each jaw has a prismatic guide 95 that lies normal to the direction of the jaw radial gripping movement, the guide tapering along the radial direction of the shaft 8.
  • the prismatic guide 95 fits for radial sliding movement in a circular groove 96 cut in said cover 93, with the jaw being guided by said pins 91.
  • Two springs 97 are received in sockets along a parallel direction to the clamping direction to bias the jaws 66 to the open position upon removal of the clamp-down force.
  • a socket 98 is provided in the area of the screw 67 on the body 69 to allow the screw head through, and rotation-preventing pins 99 ensure an orientated setting of the body 69 within the casing 94.
  • the shaft- gripping surfaces 100 are semicircular about a center which is offset toward the opposite jaw with respect to the centerline of shaft 8, and are slightly roughened with circular cross-section knurled formations .
  • the wellhead and drive disassembling/re-assembling for servicing is effected, upon the shaft 8 being stopped from rotating, by operating the screw 38 to close the clamp 10 such that its jaws 35, 36 will grip the shaft; the jaws self-centering themselves around the shaft without damaging it.
  • a conventional device is used for loosening the coupling 7 and releasing the connection between the shaft 8 and the rotating tube 5 or 46.
  • the sleeve 16 static seals 17 and oil seals 20 of the stuffing box 9 can be slipped off for quick replacement.
  • the tongue 13 would not interfere with removal of the tube 5 because of the slot 34 provided in the hub 27.
  • holes 26, in addition to being useful to tap off leakage past the oil seal 20 or the gasket 24 located upstream, may be used to introduce fluid, advantageously oil, under a pressure in order to enhance the sealing action of the affected oil seal 20, the pressure being propagated to the next oil seals in the direction toward the thrust bearing 18.
  • the ring 22 When the packing 50 is employed, the ring 22 would be retaining the packing 50' and detent rings 52 for assembling. For disassembling, the ring 22, by acting against said detent rings 52 and the fully compressed spring 53, would urge the compressed packing against the inner wall 51 of the box 9 and loosen it, thus allowing it to be removed as a whole.
  • the stuffing box operates as explained here below.
  • the packing 50 Upon assembly, the packing 50 would be forced by the spring 83 against the axial retainer ring 79 and ledge 80; the packing bein'g compressed between the outside diameter of the rotating sleeve 61 and the bore in the body 73.
  • the sleeve turns together with the shaft 8 and the gasket 76 with labyrinth 77 to stop slime in the crude oil being lifted from reaching, under the pressure, the static seals 64 between the shaft 8 and the sleeve 63 at the top end of the head.
  • the additional axial retainer ring 78 is utilized as the packing and internal components of the stuffing box 60 are taken out; it functions as an axial retainer to prevent components from coming off.
  • the split casing 81, 82 allows the spring to preload the packing at the same time as it prevents overloading the Spring 83 should the backpressure of the clean oil outflowing from the hole 75 vanish while in operation.
  • the axial thrust would be transferred from the packing 5 to the casing, and thence directly to the ring 84; from this ring, it would be further propagated to the axial thrust bearing 18 via the axial middle ledge 87.
  • the thrust force would leave the lip seal 86 unaffected and free to cling firmly; nor would it affect the seal ring 88, because the axial middle ledge 87 transfers the thrust directly to that portion of the seal ring which is strongest in the axial direction.
  • the ring 88 stops the clean lube oil from entering the upper chamber outside the stuffing box 60, and the lip seal or oil seal 86 allows the clean lube oil from the hole 75 to flow through, but prevents clean oil and ' crude oil from flowing back to the bored ring 84.
  • the lip or oil seal 86 would not wear out, because in general, well pressure only makes itself felt while the shaft is held stationary.
  • the clean lube oil to the packing is admitted through the hole 75 and distributed between said seal ring 88 and the packing 50 to also fill the annular chamber inside the split casing 81, 82.
  • the lube oil pressure is maintained above the well pressure to prevent dripping past the packing to the head, so that the dripping is conveyed into the well and the contact between the packing and the sleeve 61 can be kept in a suitable condition for proper performance and a long life.
  • the hole 74 is used for draining the stuffing box 60 before disassembly, thereby avoiding undesirable splashes as may foul the thrust bearing 31 and besmear the operator.
  • said hole allows the stuffing box 60 to be flushed clean with its internal components and the packing in place before the well is re- started.
  • the shaft locking clamp 65 with its self-centering jaws 66 is operated by first tightening down the screw 67 to urge the clamp body 69 in a radial direction of the shaft 8 against the jaws 66 and cause the latter to close around the shaft 8 along normal directions to the body direction of displacement.
  • the contact between the body and the jaws occurs across the inside taper 68 of ' the body and the mating outside taper of the jaws 66.
  • the jaws will be guided in their movement toward each other by the taper 68, the prismatic guide 95, and the pins 91 in the slot 92.
  • the springs 97 will move the jaws 66 away as the body 69 is pushed back by turning the screw 67 in the opposite direction.
  • Advantages of this invention are that: by having the stuffing box 9 mounted below the thrust assembly 6 and the drive components, full operational control of the rotating seals 20 or 50 and the gasket 24 is achieved; by having the thrust assembly placed at the top, with the inner components of the stuffing box 9 removable through the top, replacement is quickly effected with only a very short well shutdown,- the operator can thus maintain a comprehensive stock of spare parts that may include the thrust assembly 6, and directly replace any worn out or failed items in a wellhead.
  • the materials used, the dimensions and construction details may be other than those described hereinabove, yet be technical equivalents thereof, without departing from the juridical domain of the present invention.
  • the tube 62/sleeve 61 combination could be manufactured as a unit, although this would entail a more complicated construction and be cost intensive .
  • clamp 10 or analogously .
  • clamp 65 could be provided, although less conveniently, as an independent unit rather than as an attachment to the body 19 of the stuffing box 9.

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  • Geology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Sealing Devices (AREA)
  • Pressure Vessels And Lids Thereof (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Earth Drilling (AREA)

Abstract

L'invention concerne une tête de commande (1) de pompe améliorée qui comporte un presse-étoupe (9) intégré, et comprend : une transmission de puissance (3, 4) couplée à l'arbre de commande (8) de pompe rotative dans un puits de pétrole brut ; un presse-étoupe (9) pour retenir la pression ; un ensemble poussée (6) conçu pour utiliser la force de traction exercée sur l'arbre de pompe. La transmission de puissance est en outre mise en oeuvre par un tuyau (5, 16), placé de manière à tourner coaxialement avec l'arbre (8) et qui présente au moins deux diamètres différents. Des joints rotatifs (20, 50) sont mis en place sur le petit diamètre extérieur du tuyau afin d'assurer une étanchéité aux fluides entre ledit tuyau et le corps (9) du presse-étoupe. Le diamètre de travail (51) des joints (20, 50) est inférieur au grand diamètre extérieur du tuyau (5, 16). Des joints statiques (17) sont prévus entre le tuyau et l'arbre (8). Les joints statiques (17) et les joints rotatifs (20, 50) peuvent ainsi être enlevés avec le tuyau et la bague de retenue (22) des joints. De façon avantageuse, un système de serrage (10) amélioré associé à la tête sert à verrouiller l'arbre de commande (8) de pompe rotative dans le puits. Ce système de serrage comprend deux mâchoires (35, 36), une mâchoire de traction (35) et une mâchoire de poussée (36), actionnées au moyen d'une vis (38) dont une extrémité agit sur une mâchoire (35) et s'engage dans un trou fileté de l'autre mâchoire (36).
PCT/IT2003/000779 2003-04-15 2003-11-26 Tete de commande de pompe amelioree comportant un presse-etoupe et un systeme de serrage integres Ceased WO2004092539A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US10/553,392 US20070051508A1 (en) 2003-04-15 2003-11-26 Pump drive head with integrated stuffing box and clamp
CA002522257A CA2522257A1 (fr) 2003-04-15 2003-11-26 Tete de commande de pompe amelioree comportant un presse-etoupe et un systeme de serrage integres
AU2003292540A AU2003292540A1 (en) 2003-04-15 2003-11-26 Improved pump drive head with integrated stuffing box and clamp
MXPA05011096A MXPA05011096A (es) 2003-04-15 2003-11-26 Cabezal impulsor de bomba mejorado con caja prensaestopas y abrazadera integradas.
BRPI0318253-3A BR0318253A (pt) 2003-04-15 2003-11-26 cabeçote propulsor de bomba com engaxetamento e conjunto de sujeição por braçadeiras incorporado

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITPCT/IT03/00233 2003-04-15
PCT/IT2003/000233 WO2004092538A1 (fr) 2003-04-15 2003-04-15 Tete d'entrainement de pompe perfectionnee dotee d'une boite a garniture integree

Publications (1)

Publication Number Publication Date
WO2004092539A1 true WO2004092539A1 (fr) 2004-10-28

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Family Applications (2)

Application Number Title Priority Date Filing Date
PCT/IT2003/000233 Ceased WO2004092538A1 (fr) 2003-04-15 2003-04-15 Tete d'entrainement de pompe perfectionnee dotee d'une boite a garniture integree
PCT/IT2003/000779 Ceased WO2004092539A1 (fr) 2003-04-15 2003-11-26 Tete de commande de pompe amelioree comportant un presse-etoupe et un systeme de serrage integres

Family Applications Before (1)

Application Number Title Priority Date Filing Date
PCT/IT2003/000233 Ceased WO2004092538A1 (fr) 2003-04-15 2003-04-15 Tete d'entrainement de pompe perfectionnee dotee d'une boite a garniture integree

Country Status (6)

Country Link
CN (1) CN1764768A (fr)
AU (2) AU2003230206A1 (fr)
BR (1) BR0318253A (fr)
CA (1) CA2522257A1 (fr)
MX (1) MXPA05011096A (fr)
WO (2) WO2004092538A1 (fr)

Cited By (7)

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US7255163B2 (en) * 2004-08-10 2007-08-14 Rivard Raymond P Convertible rotary seal for progressing cavity pump drivehead
WO2011015911A3 (fr) * 2009-08-06 2011-07-28 Gadu Inc. Ensemble presse-étoupe
EP3128124A1 (fr) * 2015-08-05 2017-02-08 Weatherford Technology Holdings, LLC Procédé et système de pompage
US9903187B2 (en) 2015-08-05 2018-02-27 Weatherford Technology Holdings, Llc Hydraulic pumping system with enhanced piston rod sealing
US10087713B2 (en) 2014-10-01 2018-10-02 Exxonmobil Upstream Research Company Internal subsurface safety valve for rotating downhole pumps
US10167865B2 (en) 2015-08-05 2019-01-01 Weatherford Technology Holdings, Llc Hydraulic pumping system with enhanced piston rod sealing
US10344866B2 (en) * 2016-02-22 2019-07-09 Baker Hughes, A Ge Company, Llc Seal assembly for abrasion resistant bearing of centrifugal pump

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US7337851B2 (en) * 2004-09-03 2008-03-04 Weatherford/Lamb, Inc. Rotating stuffing box with split standpipe
CN101341311A (zh) * 2005-12-14 2009-01-07 Sai液压股份有限公司 用于油井泵驱动头的改进的填料箱
WO2008017210A1 (fr) * 2006-08-04 2008-02-14 Jun Liu Dispositif d'étanchéité mécanique d'une pompe à vis à commande directe par moteur
US7559359B2 (en) * 2007-08-27 2009-07-14 Williams John R Spring preloaded bearing assembly and well drilling equipment comprising same
UA109683C2 (uk) 2010-12-09 2015-09-25 Зміщений клапанний отвір у поршневому насосі
USD687125S1 (en) 2011-08-19 2013-07-30 S.P.M. Flow Control, Inc. Fluid end
CA2863563C (fr) 2012-02-01 2021-10-19 S.P.M. Flow Control, Inc. Extremite fluidique de pompe avec partie de bande integree
USD679292S1 (en) 2012-04-27 2013-04-02 S.P.M. Flow Control, Inc. Center portion of fluid cylinder for pump
CN102853083B (zh) * 2012-09-25 2015-07-15 福田雷沃国际重工股份有限公司 一种动力头防泥浆密封装置
US10465678B2 (en) * 2016-02-05 2019-11-05 Graco Minnesota Fluid pump leakage diversion
CA2967606C (fr) 2017-05-18 2023-05-09 Peter Neufeld Boitier d'etancheite, appareils connexes et methodes d'utilisation
CN109736756B (zh) * 2019-03-06 2024-01-12 无锡恒信北石科技有限公司 一种应用全金属螺杆泵的智能化采油系统

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US10087713B2 (en) 2014-10-01 2018-10-02 Exxonmobil Upstream Research Company Internal subsurface safety valve for rotating downhole pumps
EP3128124A1 (fr) * 2015-08-05 2017-02-08 Weatherford Technology Holdings, LLC Procédé et système de pompage
US9903187B2 (en) 2015-08-05 2018-02-27 Weatherford Technology Holdings, Llc Hydraulic pumping system with enhanced piston rod sealing
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US10619464B2 (en) 2015-08-05 2020-04-14 Weatherford Technology Holdings, Llc Hydraulic pumping system with detection of fluid in gas volume
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WO2004092538A1 (fr) 2004-10-28
AU2003292540A1 (en) 2004-11-04
CN1764768A (zh) 2006-04-26
AU2003230206A1 (en) 2004-11-04
MXPA05011096A (es) 2005-12-12
CA2522257A1 (fr) 2004-10-28
BR0318253A (pt) 2006-05-23

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