JPS62501226A - Oil well pipe connector - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] Oil well pipe connector This invention was filed in November 1984 with an earlier application PCT/US This is a continuation-in-part of No. 84101936.

Specification [Technical field J A normal threaded pipe coupling is considerably larger than the outside diameter of the pipe fitting that contacts it. stomach. Especially in the case of oil wells with many casings and pipes, It's good. However, in the case of oil wells, it is not found in normal surface piping systems. There are various kinds of eel v) about. SI size punching string including couplings Do not pass through the holes made by the drill or the rings that have already been placed. Must not be too expensive. Furthermore, there is a distance of 12 mm between the hole and the maximum diameter of the operating string. Create a large flow area in the annular cavity formed by the gap. It must be ensured that the friction of the flowing fluid does not create undue pressure effects. Must be. In addition, the oil 41 drilling string is one of the hollow pipes suspended in the oil well. must be able to withstand the axial tensile and compressive loads caused by the

Additionally, well drilling strings are subject to external fluid pressures that are stronger than internal pressures. Trying to be crushed. For the reasons mentioned above and other reasons, the diameter of the end was made thicker. Expensive connectors are used to operate under these constrained conditions. place However, the outer diameter of the pipe 111 that connects it is made larger than the outer diameter of the pipe 111 that connects it. The result is that it must be done. , 11 without diameter end, fitting Attach an external screw on one end and an internal mating screw on the other end to secure the external part of the threaded part. There is a pipe connector whose diameter is the same as the outer diameter of the middle part of the pipe body. However, these high Trill FJ Premium (HVdrill HJ P remiUS) pipe connector For AIP (non- Upset A P I) Pipe connection l! The tensile strength in the axial direction is small compared to the It is about 42%. According to a typical oil TT pipe program, the pipe diameter limit is 5 1/201) X27/80DX1.6D. The application along with the present application “Pump the Moon” 27/8' OD

60DX1.050D can also be installed. It is the representative program mentioned above. It can be installed very economically and efficiently at a cost that is not achievable with RAM. It is. This reduces the tonnage of tIA material consumed during oil well production. tube wall thickness When a fluid pressure horn is applied to a pipe that is not thinned, the pipe wall created by the fluid pressure The stress in the axial direction inside the pipe is approximately half of the stress in the circumferential direction generated inside the pipe by the same pressure. be. Therefore, if the mechanical axial stress of the same degree exceeds the circumferential stress, such as a whistle blower, You can add it without any problem. Attach screws to fittings of pipes that have not been up-set. If the diameter of the tube is reduced by increasing the diameter The sharpness can be further reduced.

Therefore, high efficiency is achieved with no problem with the sealing performance of the connector due to fluid pressure. There is a need for flat seam tubular connectors.

[Background entertainment technology] A flat seam tubular connector has the same inner and outer diameters as the pipe joint to which it connects. There is.

Manufactured by HydrN Co. and protected by many patents. The tubular connector, which has a flat connection, has a first straight thread and a first straight thread. Straight through the hole (y second ri straight screw and two joints on the tube / i II + f There is one that consists of fi and a tapered joint seal, but this is According to published data, the tube wall has only 42% axial strength. be.

Mark t%A, P, 1. For pipe FB#A vessels whose outer diameter is not thickened, the outer diameter is the outer diameter of the pipe body. However, like the previous one, it only produces about 42% efficiency. I can't perform. A, P, I.

Later "folded" collar outer diameter increases clearance between well drilling strings However, the outside diameter of the “folded” part is considerably larger than the outside diameter of the tube body. It has become.

It has a tapered thread and when properly assembled, the small end of the external thread and the internal To provide a connector that creates a recess saw between the large end of the screw and maximizes efficiency. No ready-to-use joint tubular connectors are disclosed in the prior art. Excessive stress Reducing the calibration strength and making the tube V thicker prevents the use of a flat connector. It is.

Therefore, the high efficiency flat fitting connector of this invention has limited radial clearance. Oil I [common for use in other pipe assemblies].

U.S. 73m ftD 3,005,414@ has fluid flow to downhole pump. Transmitting tubular wellbore strings and power harnessed from downhole pumps A string that sends fluid to the surface and a string that sends oil++ fluid from the pump to the well head. The third string is mentioned. In this invention, three pieces are arranged inside a large casing. Although parallel strings are described, using flat connection chambers arranged concentrically There is no 2vt for and.

[Disclosure of invention] This invention is a joint that does not connect the bulging part of an oil well, etc. It fits into the tapered threads formed inside both ends of the pipe fitting part! ! External with data bar A connector having a threaded tubular coupling is provided.

The coupling is made of a material that is stronger than the material that makes up the pipe joint, and the adjacent 9? The stress in the circumferential direction at the small end of the male screw, which has a thinner wall than the mold, is increased to create a seal gA. This increases the sealing force between screws mounted on each other in the area. mosquito By using a material with a strength of 80% for the coupling, the male It shall withstand an axial load higher than the axial load of 61 on the screw. Its high hardness increases wear life.

Tensioning threads on non-Eg tubes with a thread flank angle typically 60” about the tube axis In order to eliminate this effect, the shape of the screw is such that its flank angle is below 15°Ll.

The correct flank angle is selected depending on the thickness of the IL wall of the tube, material strength, etc. Determine.

Widely commercialized worldwide in 30 years in oil field development, space engineering, and nuclear industry. A series of successful U.S. special issues starting with Nos. 2,766 and 829. +As mentioned in FI, the taper of the external thread is smaller than the taper of the internal thread. The angle of the Maximum sealing effect is achieved in the lowest possible pressure range, which minimizes the load. That's how it is. This invention also utilizes this feature in combination with numerous other features. Ru.

Therefore, the first screw engagement begins with the external screw threaded at the small end. At the same time, a radial gap relationship appears at every location between the inner and outer threads. connection When tightening the pipe in the direction of complete assembly, the threads will make contact from the small end to the pipe fitting. It gradually increases in this direction. The dimensions of the screws are such that the screws on the big end will connect when fully assembled. The circumferential stress inside the pipe joint becomes smaller than the circumferential stress at the small end of the male thread. So, 1[Iideally, it should be proportional to each yield strength.

If the flank angle is set to an angle that does not tend to pull out, A, P, 1. used in 0.0556 inch 10 turns and 0.1712 inch 8 turns as shown. Use a regular pipe fitting V, not a container one, so that the thread depth is 0.030 inch. You can use shallow screws. Also, if the depth of the ridge is shallow, the coupling wall Since only a very small portion is cut to form the thread, the connection is highly effective. Also, since the coupling wall thickness can be used, it is possible to use a coupling with a thinner wall thickness. It is possible to improve the directional gap and create a connector with a flat joint that has even higher performance.

Excessive circumferential direction of one of the threaded members to be fitted together before they are fully assembled The thickness of the wall near the small end of the threaded screw is inversely proportional to the strength of each material to relieve stress. The dimensions are as an example.

Since the elastic modulus is almost the same for both members, both members have their respective material strengths. subject to stress of the same proportion as the degree.

If the innermost inner diameter of the connector is -ma, the inner diameter of the coupling should be The diameter of the standard fluid flow of the tube may be smaller than the inner diameter of the step-child For example, if the coupling is larger and shorter than the achieve. However, if axial connection strength is important, the inner diameter of the coupling a! Make it smaller than the quasi-flow diameter and lengthen the coupling to 95% to 100% % efficiency connector. , the internal thread of the pipe fitting accepts the coupling The coupling should be of appropriate size and selected from several types of couplings when used. parable For example, use a short coupling at the bottom of the string to maximize internal clearance and By using a long coupling at the top of the string, to accommodate large axial loads based on the application of

The coupling has a crotch shoulder that comes into contact with the VA end of the pipe joint when assembled. , its shoulders are determined by the length of the assembly, torque capacity, or bending strength. The selection is made based on necessary conditions such as size.

[L of the drawing! lll’l explanation J FIG. 1 shows a longitudinal sectional view of a connector according to the invention.

FIG. 2 shows the shape of the screw according to the invention.

FIG. 3 shows the thread shape of a conventional pipe connector.

[Detailed description of the invention 1 Figure 1 shows a tapered external thread 3 at the top and a similar thread 4 at the bottom, connecting the tube body 8. The tapered internal threads 6 and 1 formed in the connection parts of 9 and 1 and the tight connection threads A pipe connector consisting of a coupling 2 is shown at 20.

The coupling 2 has an inner diameter 10, an upper end 11iiN, and a lower end surface 12. When the diameter is that required to pass the industry standard "drift bar", this The end faces of the screws do not extend over the entire length of the internal screws 6 and 1. Root diameter of the last engaging screw 1 2 and the outer diameter of the tube, the connector is The axial tensile strength is more than three-quarters of the strength of the pipe wall, and the efficiency is over 75%. There is.

If the axial strength of the connector must be increased, the coupling 2 should be The diameter is shown at 13, the upper end is at 14, and the lower end is at 15. Ru. By thus stretching the coupling over the full effective length of the internal thread, Therefore, the strength of the pipe wall is equal to /u, and the axial strength of the connector is close to 100% efficiency. provide.

The length of a normal pipe II is more than 60 times the length of the coupling connected to it. , the cost of the entire tube body is much stronger than the material that forms the coupling and the fitting. It can be formed without increasing the usage. High strength material for coupling 2 By using a material, the axial strength of the joint 20 can be increased. The reason The reason is that the strength of the neck 16 of the coupling is increased σ and the crushing resistance of the end 12 of the tube is increased. This is because as the tensile strength increases, so does the tensile strength. Furthermore, the tensile strength of the contactor has been increased. For this purpose, the load supporting flank angle is 75° with respect to the tube axis as shown in Figure 2. The shape of the screw is similar to that used for passing through the oil pipe as shown in Figure 3. Fit it into the.

The shape shown in Figure 3 has a barge support angle of 60° with respect to the axis of the tube. The angle between a line perpendicular to this and a line drawn at right angles to it is 30°. office corner Assuming 5゛, vector analysis shows that the tensile strength of the shape shown in Figure 2 is 3 It becomes 2172f8 as shown in the figure. Decreasing the flank angle will improve the tension You don't have to worry about it. The thinner the threaded part is, the more When the flank angle is set to 0', the tensile strength becomes weaker, but the load Φ supporting flank The smaller the corners, the less concern you have about shifting thin-walled connectors.

Use the smallest seal diameter on the smallest diameter connector to minimize axial fluid loads. The external thread taper is very slightly smaller than the internal thread taper. . Then, the wall adjacent to the pipe connection wall 11 is thicker than the wall of the adjacent coupling. radial compression of the coupling at the end face 12. Therefore, the set When standing, the end face 12! Due to the difference in thickness from 117, the elastic modulus is almost the same. Even if you think of it as one, l! 17 compresses more than l1iW&. coupling to tube body Since the connection gl1g or 9 is made of a stronger material, JH is used for 12 and 11. The thickness of the wall can be made such that the stress in the wall is in the same proportion as its yield point stress.

If the external thread taper is smaller than the internal thread taper, the external thread and internal thread In other words, the small end at 12 and the internal thread at 17 first make contact. continue As the screws are assembled, the contact of the screws progresses toward the tapered end h. The screws at 8 are fully engaged. Further fit slightly τ, the end of the pipe fitting. fully assembled by creating a predetermined circumferential stress in section 18 and The compressive circumferential stress is brought to the first desired value, and at the same time the tube between 17 and 18 is the tensile circumferential stress in the walls of the joint is set to a second desired value smaller than said first chain; I will make it happen. These desired values are set in the same ratio as the unit yield strength of each material. Make the connection the strongest possible.

FT# Hand tighten!・Luke 14.5 (WD) 1/2 additional power tightening turn- Initial taper of PDY/3700 external thread -T-18DY-Inji/Wheein (about fl child) L In the formula W - tube wall thickness, inches D - outside diameter of tube, inches Y - Unit yield strength of tube, psi Coupling unit unit yield -1,45 Pipe unit yield strength ■ - first internal thread taper; inches/feet (about diameter) L-Length of thread engagement part P-thread load, inches E-elastic modulus The connector 20 has a shoulder 18 formed at the end of the tube connection part 9, and A shoulder 19 can be formed intermediate between the joint 4 and the outer diameter 21 of the coupling 2. . For assembly as shown in FIG. 1, interlocking threads are formed. Another song When attempting to increase the bending strength or torsional strength, the shoulder portion 18 should be and 19 should touch.

Copy and translation of amendment) Submission form “ (Patent Law Article 184-7, Paragraph 1) July 23, 1986 Commissioner of the Patent Office Kuro 1) Akio 1. International application number: PCT/US 85100260/2, title of invention: For oil wells Pipe connector/ 3. Patent applicant Address: American Congregation IN 77092 Mr. Tech4nos Name: Watsutu, John down 2f Nationality: United States of America/ 4. Agent Address: 105 = 1-1-21 Nishi-Shinbashi, Minato-ku, Tokyo June 20, 1986 Day 6. List of attached documents (1) One translation of the written amendment Battle of the scope of claims 1. There is a tapered external thread inside both ends of the f2 joint part to be connected. It is equipped with a tubular coupling adapted to fit with an internal thread with a The thickness of the wall should not be increased near its ends, and the The inner diameter of the ring is 9! Connects 1-ton oil pipes, etc. that are smaller than the inner diameter of the joint. Connector.

2. The coupling is made of a material that is stronger than the 4Ari that makes up the tubular joint. The invention according to claim 1 consisting of:

3. Take the shape of a thread, and place the load-supporting flank on the axis of the pipe, facing the thread. Claims having an angle larger than the flank angle [11 paragraph 1 or f, 2 Invention of Section.

4. Claim No. 4, wherein the load supporting flank angle is 75° or more with respect to the center axis. Invention of Section 3.

5. A claim further characterized in that the taper of the external thread is smaller than the taper of the internal thread. 1I11 Invention of item 1 or 2.

6.Furthermore, when fully assembled by providing an R section on the coupling and fitting the screws. Claim 1 or 2 in which the edge of the part @III'f is in contact with the end of the part invention of.

7. Tapered external threads provided inside both ends of the pipe joint to be connected. a tubular coupling adapted to mate with the internal thread; The ring is made of a material with higher strength than the material that makes up the pipe fitting, and when fully assembled. For the thickness of the f1 wall near the small end of the male thread, the thickness of the tube wall at the front two small ends is determined respectively. A connector that connects oil IF pipes, etc., in a manner that is inversely proportional to the strength of the materials used.

8. Adjust the size of the screw and shoulder to account for the circumferential compressive stress at the small end of the fin screw. According to claim 6, the material is made to have a hardness similar to that of the material n constituting the coupling. invention.

9. A claim in which the inner diameter of the coupling is larger than the fluid flow diameter of the pipe joint. The invention set forth in item 1 or 2.

10. Tube fitting at the root of the thread adjacent to the final engagement thread at the small end of the taper. The strength of the joint is determined by setting the thickness of the wall of the hand part to 17, which is the same as the wall of the pipe joint part in the middle part. is equal to the axial strength of the tube wall.

11. Equipped with a tapered external thread. It is a connecting device equipped with a tubular coupling that fits into an internal thread with a hole. When the connector is completely assembled, the small end of the external screw and the large internal screw The circumferential stress with the end is in the same ratio as the yield stress of each material forming the thread. A connector that connects one oil pipe, etc. with 41 dimensions and materials.

12. The connector according to claim 11, wherein the ratio is 75% or more.

13.1 Number of turns from pongee to power red Multiply by the medium fermentation strength (bond per square inch) of the tube material. The invention according to claim 11, wherein the value is equal to the value divided by 3700.

14. The i-bar (feet in inches) for the external thread's vi diameter is the internal thread's be equal to the taper (inches per foot) in diameter and outside the tube to 18. Multiply the diameter (in inches) by the yield strength of the pipe material (bond per square inch). Divide by the elastic modulus of the tube material (bonds per square inch) and calculate the thread engagement. The invention according to claim 11, which is smaller than a clam obtained by dividing the size by the length (inches).

15. A double coupling suitably connected between said upper and lower external threads. 1, 2, or 11 of the claims. The invention described.

Supplementary Procedures (Method) March 9, 1986 Commissioner of the Patent Office Kuro 1) Akio 1.Display of the incident PCT/US 85100260 2. Name of the invention Oil well pipe connector 3. Person who makes corrections Relationship to the incident: Patent applicant Address: Texas Hyuston Northwest, 77092, United States Freeway 10700 Suite 105 Name: Watts, John Taurine 4. Agent Address: 1-1-21-6 Nishi-Shinbashi, Minato-ku, Tokyo 105, Subject of amendment [Patent Law "patent applicant column" and "typeprint Translation of Paragraph 1 of the specification, written by ”International Search Report

Claims (15)

[Claims] 1. Tapered external threads provided inside both ends of the pipe fitting to be connected. a tubular coupling adapted to mate with an internal thread; Oil-driven well pipes, etc. that are made so that the thickness does not increase in the areas near both ends. Connector to join. 2. The coupling ring is made of a material that is stronger than the material that makes up the tubular step. The invention according to claim 1. 3. In the form of a thread, the load-bearing flanks are aligned with the axis of the tube and opposite the threads. The invention according to claim 1 or 2, wherein the angle is larger than the flank angle. . 4. Claim No. 1, wherein the load supporting flank angle is 75° or more with respect to the axis of the tube. Invention of Section 3. 5. Further, the taper of the external thread is smaller than the taper of the internal thread. The invention set forth in item 1 or 2. 6. Furthermore, when fully assembled by providing a shoulder on the coupling ring and fitting the screws, The invention according to claim 1 or 2, wherein the end portion of the pipe joint portion is in contact with the end portion of the pipe joint portion. 7. Tapered external threads provided inside both ends of the pipe fitting to be connected. a tubular coupling adapted to mate with the internal thread; The ring is made of a material with higher strength than the material that makes up the pipe fitting, and when fully assembled. The thickness of the tube wall near the small end of the male thread is the thickness of the tube wall at the small end, respectively. A connector that connects oil country tubular goods, etc., in a manner that is inversely proportional to the strength of the material. 8. The size of the thread and shoulder should be adjusted to reduce the compressive stress in the circumferential direction at the small end of the male thread. The invention of claim 6 is made of a material having a yield strength close to that of the material constituting the spring. Akira. 9. Claims in which the inner diameter of the coupling ring is larger than the fluid flow diameter of the pipe joint part. The invention set forth in item 1 or 2. 10. Tube fitting at the thread valley adjacent to the final mating thread at the small end of the taper The thickness of the wall of the hand part is the same as the wall of the pipe joint part in the middle part, and the strength of the joint is The invention according to claim 1 or 2, wherein the strength is equal to the axial strength of the wall. 11. A taper provided within both ends of a pipe fitting that has a tapered external thread and is to be connected. A connector comprising a tubular coupling adapted to mate with an internal thread, the connector comprising: The circumferential distance between the small end of the external thread and the large end of the internal thread when the connector is fully assembled. Dimensions such that the forward stress is in the same proportion as the yield stress of each material forming the thread. A connector that connects oil country tubular goods made of high quality materials. 12. 12. The connector according to claim 11, wherein the ratio is 75% or more. 13. The number of turns from hand-tight to power-tight to the thread lead (inch) outside the pipe. Multiply the diameter (in inches) by the unit yield strength (bonds per square inch) of the tube material. The invention according to claim 11, wherein the value is equal to the value obtained by dividing the sum by 3,700. 14. Taper (in inches per foot) relative to the diameter of the external thread to the diameter of the internal thread. equal to the taper (in inches per foot) on the diameter, and the outer diameter of the tube to 18. (inches) multiplied by the yield strength of the tube material (pounds per square inch) divided by the elastic modulus of the tube material (bonds per square inch) and then calculates the thread engagement. The invention according to claim 11, wherein the value is smaller than the value obtained by dividing by the length (inches). 15. A coupler with a coupling ring suitably connected midway between said upper and lower external screws. Claims 1, 2 or 11 consist of several tubular members. The invention described.