WO1998042945A1 - Arbre d'entrainement rotatif pour pompe de fond - Google Patents

Arbre d'entrainement rotatif pour pompe de fond Download PDF

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Publication number
WO1998042945A1
WO1998042945A1 PCT/CA1998/000258 CA9800258W WO9842945A1 WO 1998042945 A1 WO1998042945 A1 WO 1998042945A1 CA 9800258 W CA9800258 W CA 9800258W WO 9842945 A1 WO9842945 A1 WO 9842945A1
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WO
WIPO (PCT)
Prior art keywords
pin
connection
box
thread
diameter
Prior art date
Application number
PCT/CA1998/000258
Other languages
English (en)
Inventor
Trent M. V. Kaiser
Original Assignee
C-Fer Technologies 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 C-Fer Technologies Inc. filed Critical C-Fer Technologies Inc.
Priority to AU68157/98A priority Critical patent/AU6815798A/en
Publication of WO1998042945A1 publication Critical patent/WO1998042945A1/fr

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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
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • E21B17/02—Couplings; joints
    • E21B17/04—Couplings; joints between rod or the like and bit or between rod and rod or the like
    • E21B17/042—Threaded
    • 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
    • E21B43/127—Adaptations of walking-beam pump systems

Definitions

  • This invention relates to sucker rods and their connections and in particular to improvements in design of the pin and box connections.
  • Sucker rods have been used in oil and gas wells for transmitting mechanical power to artificial lift devices used in the production of oil and gas.
  • Sucker rods generally transfer power by axial load, driving pumps with a reciprocating motion along the well bore (e.g., beam or rod pumps).
  • sucker rods In recent years, there has been increasing use of sucker rods to drive pumps that operate in a rotary motion (e.g., progressing cavity pumps). This rotary type of pumping transmits power by a torsional load, or torque, along the rods.
  • Fittings for connecting together a series of sucker rods to reach the downhole pumps in the formation from which fluids are being pumped have long been standardized, and conventional fittings include a uniform diameter thread and a shoulder on which the pin end and box end meet
  • An example of this type of connection can be found in U.S. Patent 1,671,458 to Wilsoa This conventional design limits the length of thread make-up and hence its ability to withstand torsional stress, which is more acute in sucker rods associated with rotary pumps than with reciprocating pumps.
  • a conventional polished rod has a partially tapered pin/box arrangement with the taper occurring at the end of the threaded section only, and with the taper obtained by reduction of the thread height and not by reduction in diameter of the threaded section as a whole.
  • the purpose of the polished rod taper is to allow the rod to penetrate through the stuffing box without causing damage to the sealing materials contained within.
  • An example of such a conventional tapered pin/box arrangement is shown in U.S. Patent 2,690,934 to Holcombe.
  • connection upset reduces the fatigue stress associated with reciprocation and the mating shoulder faces of the box and pin provide a positive make-up ind cator and prevent the connection from "breaking out” during operation.
  • High torque capacity is a secondary consideration in the industry-standard design.
  • the space occupied by the coupiing within the annulus through which fluids are drawn to the surface diminishes the space available in the annulus for production fluid to flow, resulting in higher friction losses in the fluid.
  • a larger coupiing diameter also increases the tubing diameter required for a desired level of production. It would therefore be desirable to decrease the space occupied by the coupling yet maintain the structural integrity needed for the coupling, while in service under axial and torsional load conditions. Eliminating the need for a torque shoulder would significantly reduce the upset ratio thereby providing more annulus space for a given tubing size or permit the use of smaller tubing for effective fluid production.
  • Reducing the coupling diameter also decreases the standoff between the rod and tubing. This reduces the fatigue weakening common in the rod body adjacent to conventional pin/box connections that are subjected to combined axial and torsional loads in well intervals with moderate to high curvature It can be appreciated tha rods in deviated wells are subjected to cyclic bending stresses as the rod rotates. Furthermore, axial tension on the rod generates a localized curvature concentranon adjacent to connections because of the standoff from the tubing wail. By reducing the connection upset ratio, the standoff is lowered, thereby decreasing the curvature concentration in the adjacent rod, thus improving the fatigue resistance.
  • the invention includes an improved sucker rod coupling or connection that eliminates the mating pin and box shoulders and provides for torque transfer solely by way of the pin and box mating threads.
  • the invention includes a connection having pin threads formed on a tapered pin body and correspondingly mating threads foimed in the bore of the box.
  • the connection includes a pin having its thread formed on a core that is outwardly tapered from its terminal end to the end of the threaded portion of the pin and a non-threaded section to accommodate a box overhang portion, whh the non-threaded portion having an outside diameter approximately the same as the largest diameter of the threaded portion and having a slightly radiused transition between the overhang and a wrench flats section of the pin.
  • the largest outside diameter of the torque make-up or wrench flats section of the pin can be no greater than the outside diameter of the mated connection.
  • the box portion of the connection is correspondingly shaped and threaded to mate with the pin with load transfer contact between the pin and box provided only by way of the mating threads.
  • the coupling can be entirely integral with a rod body, i.e. pin end formed on one rod body end and box on the opposite, or could include a separate box connector having two opposing boxes for mating with rods having pins formed on both rod ends.
  • the invention further includes a method for optimizing the dimensions and configuration of a connection which eliminates the need for a torque shoulder.
  • the method includes matching the wrench flats section diameter to the sucker rod to be coupled, selecting a thread profile or form and thread length, and selecting bore and core tapers to match the thread length and profile.
  • One feature of the method is selection of a thread form for the connection which, when pin and box portions are engaged, results in contact on both the load and stab flanks of the thread to provide for load transfer between rods to occur in the mated threads.
  • Figure 1 is a side view of a sucker rod pin formed in accordance with the instant invention
  • Figure 2 is a side view of a sucker rod mated connection formed in accordance with the instant invention
  • Figure 3 is a side, cross sectional, schematic view of a box and pin mated connection illustrating the connection geometry
  • Figure 4 is a side view showing a preferred thread form for the mated connecnon of Figure 2;
  • Figure 5 is an exploded view showing the detail of a pref ⁇ red thread fbim for use in the connection of the invention;
  • Figure 6 is a graph showing radial load on a coupled rod as a function of the depth of the box counter bore for a one inch rod using a 1.25 inch connection in accordance with the present invention
  • Figure 7 is a graphical comparison of two prior art connections with a connection in accordance whh the present invention illustrating improved area available around the connection for production through production tubing.
  • connection 10 is shown formed on the end of rod body 12 and includes a make-up section 14 having wrench flats 16 for assembling and torquing up the connection.
  • wrench flats 16 Conventionally, the minimum diameter across the centers of the wrench flats marches or is only slightly larger than the outer diameter of the rod body
  • the pin 10 includes a continuous pin thread 20 formed on tapered core 22.
  • the pin thread 20 and tapered core 22 extend from terminal end 24 of the pin up to a short unthreaded pin connection entrance section 26.
  • the pin entrance section 26 preferably includes a radiused
  • connection 29 is shown having opposing entrances 26', box 30 mated with a pair of pin ends of a sucker rod string.
  • the box 30 includes an unthreaded entrance 26" and a tapered bore 1 having a continuous thread 32 formed for mating with the pin thread 20
  • the connection can be made either with
  • a rod forming opposing pin ends on the rod body and providing a separate box having opposing boxes for mating with the rod body pin ends or by providing a rod body with one shaped pin end and an opposing end shaped as a box.
  • a coupling seal such as seal 25 illustrated in Figure 1.
  • connection of the instant invention can be configured to provide the minimum overall connection diameter while providing appropriate strength to transfer the full load capacity, in
  • connection should be configured for a particular rod body size. It has been found that high torque loads can be transferred through a connection without including a torque shoulder in the connection using a tapered pin core and box bore and using only the threaded interfiice for load transfer by choosing an appropriate taper and thread length for the connectioa It is also advantageous to
  • Figure 4 schematically illustrates connection geometry and the manner in which a tapered thread core is used to produce radial interference when the pin 10 is advanced in the box 30.
  • One key feature of the invention is the inclusion of box overhang 34 outside of the threaded engaged 150 length of the coupling.
  • This overhang 34 produces a radial force concentration at the mated connection entrance section 26'. Because the box wall is thinnest in the mated connection entrance secuon 26', the lowest inward radial forces are seen in this section, some of -which are transferred from the overhang 34. It has been found that an optimal length of the overhang 34 can be determined using bending wave equations as described below. 155 Although any thread design can be used, there are some thread types that are known to be more effective at transferring torque.
  • the threads 20 and 32 preferably include straight flanks, e.g., load flanks 36 and stab flanks 38 and a flat root/crest, e.g., pm crest 40 and box root 42 as best seen in Figure 5.
  • the thread height should be kept small to minimize the effect of the thread on coupling wall thickness.
  • a key feature of the design 165 optimiza t ion method of the invention is to use as a model for the coupling load a thick-wall- pressure-vessel. It has been found that, although a coupling is not a pressure-vessel, mathema t ical models developed for stresses in such a vessel lead to design results that are effe ⁇ i ve t o produce a coupling capable of effe ⁇ ive torque transfer and of sufficient structural i ntegri t y to withstand the ⁇ gorous forces to which a sucker rod conne ⁇ ion is subje ⁇ in use. 170 Critical Sections Rod Body 12
  • the rod body section is a circular section. Hollow rods have an opening down the centre of the rod.
  • the rod body section capacities are given in terms of the rod diameter and rod bore diameter as follows:
  • the ultimate se ⁇ ion capacity gradients can be shown to be: dF submit m(d ⁇ - ⁇ z. dz ⁇ ⁇ Ty 2
  • dc is the outside diameter of the box.
  • the maximum end diameter to match the rod body 12 capacities can be determined, assuming similar material strengths for the rod and box: d * ***! ⁇ * ⁇ d r
  • the box diameter is expressed in terms of the nominal rod diameter and an upset parameter, ⁇ :
  • the thread efficiency fa ⁇ or ⁇ indicates what proportion of the thread cone carries the load. For fully engaged V-threads, the thread efficiency approaches 100%. For square threads, the thread efficiency is roughly 50%, and for partially engaged V-threads the thread efficiency can be 25% to 50%. Assuming a 50% thread efficiency is slightly conservative for the thread type 240 preferred for this application.
  • the thread se ⁇ ions 20 and 32 will fail when the stress state on the entire thread se ⁇ ions 20 and 32 (i.e. on all threads) reaches the yield limit:
  • the coupling is expanded by radial interference as the pin is advanced into the box, developing the radial stress required to produce the circumferential friction force.
  • the radial force that can be developed is limited by the strength of the coupling material, and by the thickness of the coupling. If the fri ⁇ ion fa ⁇ or is insufficient, or the length of the connection is
  • Torque is developed by fri ⁇ ion produced by the radial load resulting from radial interference.
  • the coupiing thickness is significant relative to the coupling diameter, so thick wall pressure vessel equations are appropriate to relate the radial force to the interference.
  • the radial interference will be assumed constant over the length of the threads. It is a simple matter to extend the design criteria to account for a linear interference 260 distribution associated with a taper mismatch between the pin and box.
  • Figure 5 shows a free body diagram of an infinitesimal interval of the coupiing subje ⁇ to radial interference.
  • the thick wail pressure vessel equations for an uncapped vessel can be expressed giving the conta ⁇ stress C in terms of the diametrical interference / (twice the radial interference), geometric chara ⁇ eristics, and elastic material properties.
  • This differential equation is the basis for two of the most important design equations for the connection.
  • the maximum allowable thread taper can be calculated to prevent a failure in the pin connection entrance section 26 of the mated co ⁇ ne ⁇ ion 29. From this calculation the threaded length can be d ⁇ ermined and the total torque transferred can be calculated from the integration of the differential equation. 80 The torque transfer rate must be greater than the se ⁇ ion torque capacity gradient at the mated conne ⁇ ion entrance 26" dT f dT dz dz
  • Equation 5 This expression is valid as iong as the coupling remains elastic.
  • the effective stress in the coupling is largest on the coupling inside diameter at the end of the thread, adjacent to the
  • the interference associated with first yield of the coupling is used to determine a coupiing geometry that can transfer the ultimate rod body 12 torque.
  • the additional plastic capacity of the connection accounts for the multidimensional stress effects resulting from the rod body 12 loads that are transferred through the coupling mid-section 14 simultaneously whh 310 the interference loads.
  • the mechanical load transfer rate is governed by the shear capacity of the critical thread sections 20 and 32 of the mated connection 29: dF ⁇ v
  • Axial load transfer requirements at the mated connection entrance 26' are similar to those for torque: dF dF dz dz
  • Thread load limits are calculated based on the assumption that the stress transferred across the critical thread se ⁇ ions 20 and 32 reaches the material yield limit over the entire
  • a thread capacity safety fa ⁇ or is determined from the quotient between the thread load capacity and the rod body 12 capacity. Since the threads are also subje ⁇ ed to large bearing forces on the thread flank, it is recommended that at thread capacity safety fa ⁇ or of at least two be maintained in the design. For most minimal ups ⁇ designs frictionai torque transfer rate considerations govern, producing thread capacity safety fa ⁇ ors significantly higher than
  • the calculations for thread capacity is based on the area of the cone defined by the thread roots. This introduces a slight conservatism in the design because this cone diameter is slightly smaller than that of the critical thread area. The difference between the
  • the ultimate axial load capacity FT of the critical thread sections 20 and 32 under pure shear is given by the following integration, using similar substitutions to those used in the torsional thread capacity:
  • the conne ⁇ ion entrance or coupling mouth extends past the thread interference zone, e.g., includes unthreaded se ⁇ ion 44 shown in Figure 3, elastic deformation energy generates an 360 additional radial force in the first threads.
  • This radial force is modest because the D/t ratio is largest at that location, where D is one half of the average of the coupling outside and inside diameters, and t is one half of the difference between the coupling outside and inside diameters.
  • the additional radial force at the mated conne ⁇ ion entrance 26' can augment the initial torque transfer and reduce the threaded length required to transfer torque, or provide a modest safety 365 fe ⁇ or in the torque transfer mechanism.
  • the box wail thickness in the counterbore is relatively small in comparison with the connection diameter, so the equations for a beam on an elastic foundation can be used to estimate the ring force produced by the overhang 34.
  • the spring stiffness, k, and wavelength parameter, ⁇ are given as: , 4Et
  • the length of the short beam, L is twice the overhang length for the coupiing L c , and P is also twice the augmentation load P c .
  • the displacement is equal to half of the diametrical interference /.
  • Solving for the augmentation load P and graphing with respe ⁇ to the counterbore length illustrates that the primary benefit is developed within 0.25 inches, which 380 corresponds to one half of the chara ⁇ eristic wavelength.
  • Coupling diameter selection The coupling mid-se ⁇ ion area is matched to the rod area using Equation 1.
  • the coupling upset is defined by the rod diameter and minimum allowable (by 390 manufacturing limits) coupling inside diameter. If a larger diameter coupiing is required to facilitate handling procedures, the coupling inside diameter is defined by the rod and coupiing diameters. Maximizing the coupling inside diameter increases the torque transferred over a given thread length, so there is no advantage to reducing the inside diameter further than necessary for a given coupiing upset. 395 Calculate coupiing yield interference: Using the seie ⁇ ed coupiing diameter, the coupiing yield interference is determined using Equation 6.
  • Thread profile selection The thread profile should then be seie ⁇ ed to define the effective friction coefficient for the fri ⁇ ional torque load transfer calculation, and the thread efficiency parameter for th critical thread section load capacities.
  • the effective friction coefficient is 400 given by Equation 3, and the thread efficiency is defined in Equation 2.
  • the thread height must be reduced as much as possible to minimize the impa ⁇ on the coupiing hoop strength and stiffness at the mated connection entrance 26'.
  • Thread dope should be seie ⁇ ed to give the minimum friction coefficient at make-up. This ensures that the torque capacity will not degrade if well bore fluids migrate into the threads over time. Connections should be made-up to the 405 specified torque limit.
  • Thread length calculations for load transfer in threads Four load transfer calculations are performed to calculate the minimum threaded length required to transfer load for all critical sections. Typically, the torque transfer criteria govem. Threaded lengths required for torque transfer are calculated using Equations 4 and 5. The threaded length based on an axial load 410 transfer criterion is calculated using Equation 7. The longest thread length evaluated from these calculations is used in the subsequent step.
  • Threaded section capacities check The thread capacities are checked by evaluating the safety fa ⁇ ors, using the threaded length determined in the previous step. Equations 8 and 9 give the ultimate thread capariry of the conne ⁇ ion. Dividing these results by the respective rod 415 body ultimate capacities gives the safety fa ⁇ ors with respe ⁇ to thread se ⁇ ion limits. If the safety fa ⁇ or is less than that desired, the thread length should be scaled up in proportion to the deficiency.
  • This torque can be used to provide an additional safety fa ⁇ or. If the thread
  • connection design is developed for a 1 inch solid rod with 435 a 0.25 inch upset conne ⁇ ion on the diam ⁇ er.
  • a material strength of 100,000 psi is assumed for the exercise, and the common values for elastic modulus and Poisson's ratio are used:
  • Step 1 Calculate the bore diameter using Equation 1.
  • Step 2 Calculate the thread interference (on the diameter) to produce first yield in the coupiing
  • 455 width to the pin and box is used to optimise the thread efficiency.
  • the threads are assumed to mate perfectly and transfer load only on the thread flanks.
  • a coarse thread pitch of 4 TPI (threads per inch) is used.
  • Equation 3 A conservative fri ⁇ ion coefficient of 0.1 is assumed.
  • the effective friction fe ⁇ or is calculated using Equation 3 :
  • the thread efficiency is the ratio of the thread shear area to the total thread area.
  • Step 4 Calculate the engaged thread length required for various critical section criteria. These equations are defined in terms of the thread pitch diameters. Therefore, the diameters used in these calculations refle ⁇ the pitch diameter of the thread.
  • the torque transfer rate criteria defining the maximum allowable thread taper is given by Equation 4. The calculation is made for the mated conne ⁇ ion entrance 26' of the coupling
  • the engaged thread length is calculated from the taper equation: d -d.
  • the axial load transfer rate criteria gives a maximum taper by Equation 7. This would not normally govem the design, but is included here for completeness.
  • the maximum taper 480 allowed by the axial load transfer rate criterion is given by: 2/7
  • Equation 5 The t o t al torsional load transfer capacity is given by Equation 5:
  • the ultimate torque capacity of the rod body is given by:
  • the value for a. is also updated to the thread pitch line, increasing its value to 0.47
  • the length based on the torque transfer rate is higher than that based on the total torque transfer. Because the engaged length calculated from the taper equation of 2.45 inches 495 is longer (Lt above), it is used in the remaining design steps because it results in the other criteria being satisfied.
  • Step 5 Check load safety fa ⁇ ors on the thread shear area using Equations 8 and 9.
  • the torsional load capacity for the thread shear area is (Equation 8) in terms of the thread pitch line geometry is:
  • the axial load capacity of the thread is compared with the ultimate rod body 505 axial load capacity.
  • the rod body capacity is: f .S ⁇ . ⁇ rowox' - Q)1 . 78,5 oo lb ,
  • Both axial and torsional safety fa ⁇ ors indicate adequate thread shear area capacity, so the engaged thread length remains at 2.45 inches.
  • Equation 10 gives a
  • Step 7 Optimisation with counterbore could be done to reduce the overall thread length.
  • the thread length can be reduced by 13% if the counterbore optimisation is used.
  • the improvement can be even greater, provided the torque transfer rate (Step 4a), or the total torque criteria (Step 4b) governs.
  • Figure 7 illustrates the beneficial end result of the conne ⁇ ion of the instant invention over prior art couplings which include a torque shoulder, where Figure 7A shows a standard 1 60 inch coupling within a typical 2.875 inch diameter tubing, Figure 7B a one inch conventional slimhole coupling and Figure 7C a coupiing in accordance with the present invention.
  • a conne ⁇ ion designed using the above optimization method for a nominal one inch sucker rod would have a maximum outside diameter of 1.25 inches (3.175 cm) and a length of 5.8 inches (14.73 cm) and will provide as much as 263 percent more flow area about the 65 coupling than prior an conventional couplings designed for the same rod body 12.
  • the redu ⁇ ion in standoff reduces fatigue stresses appreciably.
  • the bending concentration is only 2.3 times the nominal curvature or 53% the bending concentration of 4.3 produced by conventional couplings.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)

Abstract

L'invention concerne un dispositif d'assemblage et un procédé améliorés qui permettent d'assembler des tiges de pompage dans un train de tiges de pompage utilisé pour entraîner des pompes de fond en vue de la production de fluides à partir d'une formation souterraine. Le dispositif d'assemblage a un diamètre externe inférieur ou égal à une fois et demi le diamètre externe de la tige de pompage. Le contact entre les filetages correspondants dudit dispositif d'assemblage est utilisé pour transférer des charges au niveau du couplage des tiges de pompage assemblées.
PCT/CA1998/000258 1997-03-24 1998-03-24 Arbre d'entrainement rotatif pour pompe de fond WO1998042945A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU68157/98A AU6815798A (en) 1997-03-24 1998-03-24 Rotary drive shaft for downhole pump

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US82337997A 1997-03-24 1997-03-24
US08/823,379 1997-03-24

Publications (1)

Publication Number Publication Date
WO1998042945A1 true WO1998042945A1 (fr) 1998-10-01

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CA (1) CA2232925C (fr)
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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1052368A1 (fr) * 1999-05-12 2000-11-15 Ihc Holland N.V. Ensemble de connection entre arbre et moyeu
EP1243829A1 (fr) * 1999-12-27 2002-09-25 Sumitomo Metal Industries, Ltd. Raccord a vis pour tube de puits de petrole
CN107152244A (zh) * 2016-03-04 2017-09-12 特纳瑞斯连接有限公司 抽油杆端部
WO2021140755A1 (fr) * 2020-01-06 2021-07-15 日本製鉄株式会社 Raccord fileté de tuyau en acier

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA3077491A1 (fr) 2020-03-30 2021-09-30 Plainsman Mfg. Inc. Accouplement a chevilles et methode d`assemblage

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE199656C (fr) *
US1671458A (en) 1925-05-19 1928-05-29 Guiberson Corp Rod joint
US2690934A (en) 1950-08-28 1954-10-05 Samuel M Holcombe Insulated sucker rod and tubing to prevent electrolysis and corrosion
USRE31123E (en) * 1977-01-03 1983-01-11 Centron Corporation Pipe section and coupling
GB2113745A (en) * 1982-01-23 1983-08-10 Benteler Werke Ag A pump rod for a pump string
GB2114187A (en) * 1982-01-23 1983-08-17 Benteler Werke Ag A pump rod for a pump string
DE3435155A1 (de) * 1983-10-03 1985-04-11 Dril-Quip, Inc., Houston, Tex. Selbstausrichtende verbindungsvorrichtung
DE3913974A1 (de) * 1988-05-31 1989-12-14 Siemens Ag Anordnung zum loesbaren verbinden zweier koerper, insbesondere zugstangenverbindung
US5348094A (en) * 1992-06-12 1994-09-20 Institut Francais Du Petrole Device and method for pumping a viscous liquid comprising injecting a thinning product, application to horizontal wells
WO1997002403A1 (fr) * 1995-07-05 1997-01-23 Harrier Technologies, Inc. Ameliorations d'installations de pompage pour puits profonds

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE199656C (fr) *
US1671458A (en) 1925-05-19 1928-05-29 Guiberson Corp Rod joint
US2690934A (en) 1950-08-28 1954-10-05 Samuel M Holcombe Insulated sucker rod and tubing to prevent electrolysis and corrosion
USRE31123E (en) * 1977-01-03 1983-01-11 Centron Corporation Pipe section and coupling
GB2113745A (en) * 1982-01-23 1983-08-10 Benteler Werke Ag A pump rod for a pump string
GB2114187A (en) * 1982-01-23 1983-08-17 Benteler Werke Ag A pump rod for a pump string
DE3435155A1 (de) * 1983-10-03 1985-04-11 Dril-Quip, Inc., Houston, Tex. Selbstausrichtende verbindungsvorrichtung
DE3913974A1 (de) * 1988-05-31 1989-12-14 Siemens Ag Anordnung zum loesbaren verbinden zweier koerper, insbesondere zugstangenverbindung
US5348094A (en) * 1992-06-12 1994-09-20 Institut Francais Du Petrole Device and method for pumping a viscous liquid comprising injecting a thinning product, application to horizontal wells
WO1997002403A1 (fr) * 1995-07-05 1997-01-23 Harrier Technologies, Inc. Ameliorations d'installations de pompage pour puits profonds

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
API SPECIFICATION, 25TH EDITION, vol. 11B, 1 January 1995 (1995-01-01)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1052368A1 (fr) * 1999-05-12 2000-11-15 Ihc Holland N.V. Ensemble de connection entre arbre et moyeu
EP1243829A1 (fr) * 1999-12-27 2002-09-25 Sumitomo Metal Industries, Ltd. Raccord a vis pour tube de puits de petrole
EP1243829A4 (fr) * 1999-12-27 2003-01-15 Sumitomo Metal Ind Raccord a vis pour tube de puits de petrole
CN107152244A (zh) * 2016-03-04 2017-09-12 特纳瑞斯连接有限公司 抽油杆端部
WO2021140755A1 (fr) * 2020-01-06 2021-07-15 日本製鉄株式会社 Raccord fileté de tuyau en acier
JP6930683B1 (ja) * 2020-01-06 2021-09-01 日本製鉄株式会社 鋼管ねじ継手構造

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Publication number Publication date
AU6815798A (en) 1998-10-20
CA2232925C (fr) 2003-04-29
CA2232925A1 (fr) 1998-09-05

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