WO2020102586A2 - Joint à haute résistance à la traction permettant de relier des tiges et des raccords - Google Patents

Joint à haute résistance à la traction permettant de relier des tiges et des raccords Download PDF

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Publication number
WO2020102586A2
WO2020102586A2 PCT/US2019/061546 US2019061546W WO2020102586A2 WO 2020102586 A2 WO2020102586 A2 WO 2020102586A2 US 2019061546 W US2019061546 W US 2019061546W WO 2020102586 A2 WO2020102586 A2 WO 2020102586A2
Authority
WO
WIPO (PCT)
Prior art keywords
rod
fitting
wedge
joint
diameter
Prior art date
Application number
PCT/US2019/061546
Other languages
English (en)
Other versions
WO2020102586A3 (fr
Inventor
James P. GORMICAN
Mitchell Hale
Keith Loss
Tobias PANEK
Original Assignee
Megalex Joint, Llc
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
Priority claimed from US16/193,657 external-priority patent/US11391312B2/en
Application filed by Megalex Joint, Llc filed Critical Megalex Joint, Llc
Priority to CA3119969A priority Critical patent/CA3119969A1/fr
Publication of WO2020102586A2 publication Critical patent/WO2020102586A2/fr
Publication of WO2020102586A3 publication Critical patent/WO2020102586A3/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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B7/00—Connections of rods or tubes, e.g. of non-circular section, mutually, including resilient connections
    • F16B7/02—Connections of rods or tubes, e.g. of non-circular section, mutually, including resilient connections with conical parts
    • F16B7/025—Connections of rods or tubes, e.g. of non-circular section, mutually, including resilient connections with conical parts with the expansion of an element inside the tubes due to axial movement towards a wedge or conical element
    • 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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B11/00—Connecting constructional elements or machine parts by sticking or pressing them together, e.g. cold pressure welding
    • F16B11/006—Connecting constructional elements or machine parts by sticking or pressing them together, e.g. cold pressure welding by gluing

Definitions

  • This invention relates generally to connectors and fixtures and, more specifically, to a High Tensile Strength Joint for Connecting Rods and Fittings.
  • the present invention comprises a joint which connects a rod and a fitting, wherein the rod and fitting are subjected to high-tension loads.
  • the invention is especially useful in constructing a sucker rod for oil wells.
  • the invention may be used, however, in many other applications, such as in pre-stressed concrete, and in tension members for bridges.
  • a sucker rod is a long rod formed of a plurality of sections, capable of connecting a pump, located at the bottom of an oil well, with a lifting device, or pump jack, located at the surface. Each section may include a rod portion and a fitting portion, each rod being inserted into a fitting.
  • a sucker rod comprises a long chain of rods and fittings and couplings. Because some wells may be deeper than 16,000 feet, the sucker rod must have very high tensile strength, so that the rod does not break under its own weight plus that of the fluid, as it is pulled up by the pump jack, and pulled down by gravity. The problem of designing a sucker rod having the necessary tensile strength is made more difficult by the fact that the rod typically must fit within a tubing of relatively small diameter.
  • the prior art has not developed a sucker rod having sufficient tensile strength, while occupying a minimal cross-sectional area.
  • a sucker rod which is stronger than sucker rods of the prior art, which incorporates advanced materials that are lighter than metal, and which still fits within a narrow tubing bore.
  • the present invention provides a joint which exhibits very high tensile strength, while minimizing the cross-sectional area required.
  • the joint of the present invention can therefore be used to construct longer, lighter sucker rods which can still lift a useful payload of fluid. It can also be used in many other applications requiring the assembly of rods capable of carrying large tensile loads.
  • the joint of the present invention is not intended to bear significant compression loads.
  • the present invention comprises a joint which includes a solid rod inserted into a fitting.
  • the rod is preferably a carbon or graphite composite, and the fitting is preferably made of steel.
  • the rod has an opening or slit at its ends, into which a wedge is inserted.
  • the internal diameter of the fitting varies smoothly and nonlinearly with distance along the fitting.
  • the internal contour of the fitting becomes parallel to the axis of the rod.
  • the wedge has a dimension which also varies smoothly and nonlinearly with distance.
  • the variation of the dimension of the wedge is substantially the same as that of the internal diameter of the fitting. That is, the contour of the fitting is substantially the same as the contour of a portion of the wedge.
  • this contour can be described by a polynomial function having an order of at least two, such that the contour becomes parallel to the axis of the rod at the narrow end of the wedge where it terminates.
  • the wedge has a cruciform shape.
  • the preferred wedge includes at least two mutually non-parallel vanes.
  • the wedge could instead have only a single vane.
  • the wedge In assembling the joint, the wedge is prepared by forming at least one slit in the rod, so that the rod can accommodate the wedge. The wedge is then inserted into the rod, causing the rod to expand or swage outward. When the rod, with the wedge inserted, is inserted into the fitting, the joint occupies virtually all the space within the fitting, at all points where the rod and wedge are present.
  • the joint of the present invention exhibits very high strength under tension.
  • the joint may also include a plug which is inserted into the fitting which prevents the rod from being dislodged with respect to the fitting in the presence of relatively small compressive loads.
  • the joint is particularly suited for use in constructing sucker rods for oil wells, because the joint can accommodate very high tensile loads, while occupying a long and narrow tubing bore.
  • the joint can also be used in applications other than in oil production.
  • the invention therefore has the primary object of providing a joint which exhibits high tensile strength.
  • the invention has the further object of providing a joint which can be used to construct a long rod, wherein the rod has high tensile strength while fitting within a tubing bore of relatively small diameter.
  • the invention has the further object of providing a joint for use in a sucker rod for an oil well.
  • the invention has the further object of providing a joint which uses a solid rod, and which thereby takes full advantage of the available cross-section of the rod, providing a structure of high tensile strength.
  • Figure 1 provides a perspective view of the joint of the present invention, showing a rod inserted into a fitting.
  • Figure 2 provides a cross-sectional view of the joint of the present invention, taken along the line II- II of FIG. 1;
  • Figure 3 provides a side view of a swaged rod, with the fitting removed, used in the present invention, the rod having a cruciform wedge inserted therein;
  • Figure 3 a provides a side view of the rod used in the present invention, showing an opening or slit formed therein, before a wedge has been inserted;
  • Figure 4 provides an end view of the rod and the cruciform wedge of Figure
  • Figure 4a provides an end view of the slitted rod of Figure 3a;
  • Figure 5 provides a perspective view of the cruciform wedge used in the present invention
  • Figure 6 provides a side view of a swaged rod, with the fitting removed, used in the present invention, the rod having a multiply-vaned wedge inserted therein;
  • Figure 7 provides an end view of the rod and the multiply-vaned wedge of Figure
  • FIGS 8A, 8B, 8C and 8D sequentially depict the steps of the preferred method of the present invention.
  • FIG. 9 is a flowchart showing the steps of the preferred method of the present invention.
  • Figure 1 provides a perspective view showing the joint of the present invention.
  • the joint includes rod 1 inserted into fitting 2.
  • the rod is formed of a composite including graphite, or other carbon, and an organic resin.
  • the graphite exists in the form of tightly- packed fibers or filaments, which maintain their identities as having individual, small diameters.
  • the organic resin is similar to an adhesive, and binds the fibers effectively into a single, solid rod.
  • the fitting is a single piece of machined metal, preferably formed of high-strength steel.
  • the steel forming the fitting preferably has a yield strength in the range of 110 ksi-140 ksi.
  • the material must not be too brittle, and must allow reasonable elongation (of the order of greater than about 15%) before failure.
  • the steel may be selected according to its corrosion resistance properties, if desired.
  • Figure 2 provides a cross-sectional view of the joint of the present invention, taken along the line II- II of Figure 1.
  • the line II- II is somewhat off-center, as will be apparent later in this description.
  • Figure 2 shows solid rod 1 inserted within fitting 2.
  • the rod includes a slit which accommodates a wedge 3.
  • the wedge is inserted within the slit, and occupies substantially all of the space defined by the slit. The wedge therefore causes the rod to be swaged outward.
  • An adhesive indicated symbolically by dashed lines in Figure 2, is provided between the outer surface of the rod and the inner surface of the fitting, as well as between the wedge and slit surfaces of the rod.
  • a plug 4 if included, is screwed into the fitting, with the aid of threads 6.
  • the plug provides resistance to small, incidental compressive forces. That is, if the assembly of rods and fittings is momentarily compressed, the plug prevents the rod from becoming dislodged and pushing into the open, larger diameter end of the fitting.
  • the plug is preferably made of metal.
  • element numbers enclosed in square brackets [ ] indicates that the referenced element is not shown in the instant drawing figure, but rather is displayed elsewhere in another drawing figure. It is an important aspect of the present invention that the wedge be smoothly curved, and that the inside surface of the fitting be smoothly curved. Also, the curvature of the wedge has substantially the same shape as the curvature of the interior surface of the fitting.
  • the internal diameter of the fitting varies smoothly and nonlinearly with distance along the fitting.
  • the wedge has a dimension which similarly varies smoothly and nonlinearly with distance along the wedge.
  • the fitting has a threaded region, at and to the right of the plug 4, and a contoured region, to the left of the plug, in which the inside surface of the fitting is contoured as described above.
  • D is the internal diameter of the fitting
  • Dthroat is the diameter of the rod plus a clearance (typically about 0.01 inches);
  • L is the length of the contoured internal diameter
  • Rdelta is (Dmax- Dthroat)/2, D max is the desired maximum internal diameter of the fitting at the point where the width of the wedge is at its maximum; and z is the distance from the start of the contoured shape of the internal diameter.
  • R deita is the increase in the internal radius of the fitting caused by the swaging effect of the wedge.
  • Equation (2) The thickness of the wedge, as a function of y, which is defined by Figure 5, is given in the following Equation (2).
  • Equation (2) the axes are different from those implied in Equation (1).
  • Equation (2) is the same for T2(y), which is the thickness of the other vane of the wedge, as shown in FIG. 5.
  • Equation (3) The width of the wedge, as defined in Figure 5, is given by Equation (3), as follows:
  • W 0 width of wedge at the narrow end (about 0.98(D throat ))-2t bondiine )
  • W max maximum width of wedge at wide end (about 0.95 (Dmax)- 2tbondline)
  • t bondiine nominal thickness of the bondline (about 0.005 inches)
  • L Wedge 0.99(L) (99% of length of the cut, L cut ) (see FIG. 3 a)
  • D max the desired maximum diameter at the maximum width of the wedge
  • D throat the diameter of the rod plus a clearance (typical clearance being about 0.01 inches)
  • Equation (3) is the same for W 2 (y), which is the thickness of the other, relatively perpendicular vane of the wedge, shown in Figure 5.
  • the wedge thickness is t max
  • W max the wedge width
  • Equation (2) yields a value of to for the wedge thickness
  • Equation (3) yields a value of W 0 for the wedge width.
  • the wedge can be trimmed, so that the measured thickness becomes the starting thickness of the wedge.
  • the internal diameter of the fitting, and the thickness and width of the wedge must vary smoothly and nonlinearly with distance.
  • the contour or shape of the inside of the fitting should be the same as the contour of the thickness of the wedge, which should be the same as the variation of the width of the wedge.
  • the desired maximum inner bore diameter of the fitting corresponding to the end of the wedge is selected according to the following criteria:
  • the cross-sectional area of the fitting is at least twice the cross-sectional area of the rod at any point along the fitting which is occupied by the wedge;
  • the maximum diameter is greater than about 1.3 times the diameter of the rod and less than about 1.5 times the diameter of the rod.
  • the maximum width of the wedge is not quite equal to the full diameter of the fitting.
  • the wedge should be relatively short and compact.
  • the length of the wedge is preferably less than five times the diameter of the rod, allowing for a shorter fitting that is less than 5.3 times the diameter of the rod.
  • substantially all of the space within the fitting, at all points where the rod and wedge are present, is occupied by the components of the invention, namely the wedge, the rod, and to a minimal extent, the adhesive. There is virtually no “air” or unoccupied space within the fitting, where the rod is present.
  • the wedge preferably has a cruciform shape.
  • Figures 3 - 5 illustrate this feature.
  • the cruciform wedge is illustrated in the perspective view of Figure 5, which shows vertical vane 50 and horizontal vane 51.
  • the vanes can be machined as a unitary part, or they could be separately constructed and suitably joined. Both vanes have a thickness which increases from left to right, as shown in the drawing.
  • the variation in thickness of each vane could be as given in Equation (2), discussed above. If Equation (2) is used to define the variation of the thickness of one of the vanes, it should be used for both vanes. In general, all vanes should have the same variation of thickness with distance along the wedge.
  • Figure 3 shows the wedge 52 inserted within the rod 53.
  • the end view of Figure 4 further illustrates the cruciform structure of the wedge, when it is embedded in the rod 53.
  • Figure 3a shows the rod 53 having an opening or slit 55 formed therein.
  • Figure 3a represents the state of the rod before a wedge has been inserted.
  • the figure also indicates the definition of the quantity t kerf , which is the thickness of the kerf, which is the material removed from the rod in forming the slit.
  • Figure 4a shows the corresponding end view of the rod of Figure 3a.
  • FIGS. 6 and 7 illustrate an example in which the wedge comprises three vanes.
  • the side view of Figure 6 shows two vanes 61, 62, and the end view shows all three vanes 61, 62 and 63.
  • the wedge has at least two vanes. It is also possible for the wedge to have only one vane. In this case, the swaging effect would occur in only one direction. This arrangement would result in a weaker rod assembly, but might be useful in certain applications.
  • the internal diameter of the fitting, and the outer diameter of the rod, and the thickness of the wedge vary according to the cube of the distance along the fitting.
  • This curvature need not be exactly as shown in the example. Rather, it is a feature of the invention that the curvature be described by a polynomial equation having an order of at least two. Such equation may represent the deflected shape of a cantilever beam under an end load.
  • the diameter of the fitting could vary with the square or the cube, or some higher power, of the distance.
  • the curvature may be consistent with the deflected shape of a beam under distributed loads.
  • a plurality of slits is formed in the rod, an adhesive is inserted in the slits, and applied to the wedges, and the wedges are then inserted into the slits.
  • the length of each slit should correspond to the length of the wedge to be inserted.
  • some of the material of the rod is removed, this material being known as“kerf”.
  • the wedges When the wedges are fully inserted, substantially all of the space within the rod is filled. More particularly, the wedges, when inserted, substantially conform to the contour of the adjacent material of the rod, to insure that virtually all of the space is filled.
  • the slits are very small relative to the diameter of the rod to not significantly weaken the rod.
  • the rod is a pultruded solid composite, and is compatible with high-temperature epoxy resins.
  • the choice of a solid composite rod makes it feasible to use high-strength carbon or graphite fibers. Since the carbon or graphite fibers fill substantially all of the cross-sectional area of the rod (until the wedge has been inserted), the present invention takes advantage of the full cross-section, and results in a stronger rod, for a given cross-sectional area. That is, the joint can
  • the high strength of the rod makes it possible to design the joint such that the rod and fitting are of relatively small diameters.
  • the rod and fitting are more likely to be successfully operated within small diameter tubes, such as the bore of an oil well.
  • the invention is not limited to a rod or fitting of any particular diameter. What is important is that the rod initially be of solid construction, and that it initially have a constant diameter.
  • the invention can be scaled such that larger and thicker rods and fittings could be used.
  • the rod has been described as graphite, or as a composite of graphite and resin, the rod may be made of another material, such as metal or fiberglass.
  • the threaded end of the fitting allows multiple segments to be connected using a standard coupling technique.
  • the joint of the present invention is intended to transfer large loads in tension, but not compressive loads.
  • the plug caps off the end of the rod, and will withstand relatively small, incidental compression loads that might otherwise cause the rod to unseat from the fitting.
  • the present invention is not limited to use with sucker rods in the oil industry. It could be used in structural applications such as tension rods for pre-stressing of concrete and other materials which are strong in compression. It could be used in making guy wires or cables. It could also be used for pre-stressed concrete structures and/or in making suspension supports, such as are used for bridges.
  • the invention can be modified in various ways. As indicated above, the number of vanes of the wedge can be varied. The materials used for the wedge, the rod, and the fitting can be changed, consistent with the requirements of stiffness. The exact contour of the relevant surfaces of the fitting and wedge can be varied, as long as the contour is smooth and nonlinear.
  • FIGs 8A, 8B, 8C and 8D sequentially depict the steps of the preferred method of the present invention.
  • the fitting 2 has been positioned within the chuck of the press machine used to assemble the joint of the present invention.
  • the rod 53 has been slid into the fitting 2 in direction "D" until the pre-determined end portion R(E) of the rod 53 is exposed beyond the threaded end 70 of the fitting 2.
  • This distance R(E) can be expressed as either a dimension, or as a length that is determined as a function of the diameter of the rod 53.
  • the optimum exposed portion R(E) should be approximately 125 percent of the length of the slit 55 (and wedge 52). As such, for 4-inch long slit/wedge, the optimum exposed portion R(E) is five (5) inches.
  • a small volume fraction ( ⁇ 5%) of small, hard spheres (herein termed“bonding beads”) made from glass or metal are added to the adhesive to maintain a minimum bond line thickness of approximately .007” to prevent the adhesive from being scraped off during the insertion process.
  • small diameter glass filaments or metal wires could be aligned lengthwise in the adhesive to serve the same function of ensuring the minimum bond line thickness.
  • the wedge 52 (or cruciform pair of wedges as depicted in Figure 4) is/are partially inserted into the slit 55 (or slits) until the pre determined end portion W(E) remains exposed beyond the face of the rod 72.
  • This distance W(E) can be expressed as either a dimension, or as a length that is determined as a function of the diameter of the rod 53.
  • the optimum exposed portion W(E) should be approximately 2/3 rds of the length of the wedge 52 (and slit 55). As such, for a 4-inch long slit/wedge, the optimum exposed portion W(E) is 2 2/3rds inches.
  • this position is reached (transitioning from the position of Figure 8B) by pulling on the rod 53 in direction -D (rather than by handling the wedge(s) 52).
  • This distance W(E) can be expressed as either a dimension, or as a length that is determined as a function of the diameter of the rod 53.
  • the optimum pre-press exposed portion W(E) should be approximately 2/3 rds of the length of the wedge 52 (and slit 55). As such, for a 4-inch long slit/wedge, the optimum exposed portion R(PE) is 2 2/3rds inches.
  • Figure 8D depicts the final positions of the wedges, rod and fitting after the joint has been pressed in direction -D by the press machine.
  • the rod 53 remains in the "rod seated position" P(F) relative to the end of the tapered portion 77 of the fitting 2, and the wedge(s) is/are in "wedge seated position" with end of 74 in the same plane as the end of the rod face 72.
  • Figure 9 is a flowchart showing the steps of the preferred method 80 of the present invention. It should be understood that the fitting [2] has first been inserted into, and secured within the chuck of the joint press machine. The rod [53] is inserted into the fitting [2] until the end is exposed by not less than dimension [R(E)] 100. Next (or at any time prior to step 104), adhesive (e.g. epoxy) and bonding beads are applied to the curved side face(s) of the wedge or wedges [52] 102.
  • adhesive e.g. epoxy
  • bonding beads are applied to the curved side face(s) of the wedge or wedges [52] 102.
  • the wedge or wedges [52] are inserted into the slit(s) 55 formed in the end of the rod [52] until they are partially inserted 104 (i.e. until [W(E)]) is reached.
  • Epoxy with bonding beads is then applied to the exposed end (portion [R(E)]) of the rod [53] 106, and the rod [53] is then slid into the fitting [2] until it reaches pre-press position [R(PE)].

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mutual Connection Of Rods And Tubes (AREA)

Abstract

L'invention concerne un joint qui présente une résistance à la traction élevée. Le joint comprend une tige pleine ayant une fente ou une ouverture dans laquelle est inséré un coin. La tige et le coin sont insérés dans un raccord. Seule une petite quantité de matériau adhésif est appliquée entre le raccord et la tige. Le matériau adhésif peut être mélangé avec des "billes" non adhésives et non compressibles qui ont un diamètre préféré afin d'assurer que l'épaisseur d'adhésif souhaitée soit atteinte entre le raccord et la tige. La surface interne du raccord présente un contour qui varie de façon continue et non linéaire avec la distance le long du raccord. Le coin a une dimension ayant un contour similaire. La forme du contour peut être décrite par un polynôme d'ordre deux ou plus. Le joint peut être utilisé pour construire une tige de pompage destinée à un puits de pétrole, ou peut être utilisé dans d'autres applications. Le joint peut supporter des charges de traction élevées, sur de longues distances, tout en occupant un trou de colonne de production très étroit.
PCT/US2019/061546 2018-11-16 2019-11-14 Joint à haute résistance à la traction permettant de relier des tiges et des raccords WO2020102586A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CA3119969A CA3119969A1 (fr) 2018-11-16 2019-11-14 Joint a haute resistance a la traction permettant de relier des tiges et des raccords

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US16/193,657 US11391312B2 (en) 2012-06-19 2018-11-16 Method for creating a high tensile strength joint for connecting rods and fittings
US16/193,657 2018-11-16

Publications (2)

Publication Number Publication Date
WO2020102586A2 true WO2020102586A2 (fr) 2020-05-22
WO2020102586A3 WO2020102586A3 (fr) 2020-08-06

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Application Number Title Priority Date Filing Date
PCT/US2019/061546 WO2020102586A2 (fr) 2018-11-16 2019-11-14 Joint à haute résistance à la traction permettant de relier des tiges et des raccords

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CA (1) CA3119969A1 (fr)
WO (1) WO2020102586A2 (fr)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4430018A (en) * 1983-04-11 1984-02-07 Technicraft, Inc. End fitting for oil well sucker rods
US4787771A (en) * 1986-04-08 1988-11-29 Allen Loy F Loaded sucker rod fitting
US6193431B1 (en) * 1997-09-24 2001-02-27 The Fiber Composite Company, Inc. Fiberglass sucker rod end fitting
US10132343B2 (en) * 2012-06-19 2018-11-20 Megalex Joint, Llc High tensile strength joint for connecting rods and fittings

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Publication number Publication date
CA3119969A1 (fr) 2020-05-22
WO2020102586A3 (fr) 2020-08-06

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