WO2022070367A1 - 管のねじ継手およびその接続方法 - Google Patents
管のねじ継手およびその接続方法 Download PDFInfo
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- WO2022070367A1 WO2022070367A1 PCT/JP2020/037353 JP2020037353W WO2022070367A1 WO 2022070367 A1 WO2022070367 A1 WO 2022070367A1 JP 2020037353 W JP2020037353 W JP 2020037353W WO 2022070367 A1 WO2022070367 A1 WO 2022070367A1
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- screw
- shoulder
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Images
Classifications
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- 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
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
- F16L15/001—Screw-threaded joints; Forms of screw-threads for such joints with conical threads
- F16L15/004—Screw-threaded joints; Forms of screw-threads for such joints with conical threads with axial sealings having at least one plastically deformable sealing surface
-
- 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
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
- F16L15/04—Screw-threaded joints; Forms of screw-threads for such joints with additional sealings
-
- 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
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
- F16L15/06—Screw-threaded joints; Forms of screw-threads for such joints characterised by the shape of the screw-thread
-
- 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
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
- F16L15/08—Screw-threaded joints; Forms of screw-threads for such joints with supplementary elements
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/10—Geothermal energy
Definitions
- the present invention relates to a threaded joint used for connecting an oil well pipe including a tubing and a casing used for exploration and production of an oil well or a gas well, and a steel pipe applied to a geothermal well using high temperature steam for power generation.
- the present invention relates to a threaded joint for steel pipes in which pins connected by threads from both ends of the ring are brought into contact with each other at the center of the inner surface of the coupling.
- Threaded joints are widely used to connect steel pipes used in petroleum industry equipment such as oil country tubular goods.
- Oil well pipes called casings and tubing are used for drilling and production of crude oil and natural gas wells, and the connection is conventionally the threaded joint 100 specified in the API (American Petroleum Association) 5B standard shown in FIG. 1A. Has been used.
- FIG. 1B is a schematic explanatory view of a threaded joint 200 for oil country tubular goods in a coupling type and in which the shoulder portions 201 at the tip of the pin are in contact with each other, which is a vertical sectional view of the threaded joint 200 of a circular pipe.
- the threaded joint 200 usually includes a tapered screw 203 at each pipe 202 and a shoulder portion 201 at the tip of the pin, which is also called a torque shoulder portion.
- the threaded joint 200 does not have the seal portion 302 as in the premium joint.
- the joint called the coupling 204 is provided with a taper screw 205 at both ends, and the taper screw 205 is screwed with the taper screw 203 machined at the pipe end of the pipe 202.
- the coupling 204 does not have the shoulder portion 303 as in the premium joint.
- the taper threads 203 and 205 are important for tightly fixing the fitting, and inserting the pin 206 with the taper thread 203 into the coupling 204 also with the taper thread 205 causes radial interference. Pin 206 is fixed in the coupling 204.
- the coupling 204 includes a male screw member called a pin 206 and a corresponding female screw member.
- One pin 206a and the other pin 206b connected to the coupling 204 are machined with a male thread as a taper screw 203 on the outer surface thereof, and each has a shoulder portion 201 at the tip thereof.
- the opposing coupling 204 has a female thread on its inner surface as a tapered thread 205 that can be screwed into a male thread.
- one pin 206a is pre-tightened at the factory until it reaches the axial center position of the coupling 204, the other pin 206b is locally tightened, and one pin 206a already tightened at the factory.
- the shoulder portion 201 of one pin 206a also serves as a stopper that provides an appropriate tightening stop position for the other pin 206b when the other pin 206b is tightened in the field.
- the shoulder surfaces at the tips of both pins come into direct contact with each other to form a high tightening torque, and the pipe 202 and the threaded joint 200 rotate while excavating a horizontal well. You can propel in the well.
- API5B Threading, Gauging, and Inspection of Casing, Tubing, and Line Pipe Threads published December 1, 2017
- API7G Recommended Practice for Drill Stem Design and Operating Limits published December 1, 1998
- the premium joint shown in FIG. 2 is composed of three regions, a screw portion 301, a seal portion 302, and a shoulder portion 303, each of which has a separate function.
- a screw portion 301 since it has an independent sealing part 302, it is highly airtight even under a high load combined load, but it has high processing dimensional accuracy and high price, so it is generally used in difficult environments such as deep sea development. Therefore, it is hard to say that it is a suitable threaded joint that satisfies both price and performance for shale development.
- the pin 101 of the API BTC screw which is the general purpose screw of FIG. 1A
- the coupling 102 are connected only by screw fitting, as compared with the threaded joint 100 of FIG. 1B.
- the threaded joint 200 in which the shoulder portions 201 at the tip of the pin abut against each other is rational in generating a high tightening torque.
- the tips of the pins 206 inserted from both tube ends of the coupling 204 are not necessarily in contact with each other, and are strictly strict. Is biased. This uneven contact causes excessive strong contact on the inner diameter side or the outer diameter side of the shoulder surface, which is the end surface of the shoulder portion 201 at the tip of the pin, in the process of tightening the screw, and the plastic deformation of the shoulder surface causes the tightening torque. It occurs from a low stage and increases the risk of reduced yield torque (see paragraph 15) and galling (metal-to-metal seizure) during tightening.
- FIGS. 3A to 3C schematically show the cross section of the shoulder portion 201 immediately before the contact at the portion A in FIG. 1B.
- Factors that affect the state of contact of the shoulder portion 201 at the tip of the pin are as follows, although the degree of influence varies. 1) Deflection of the pin tip downward (inner surface side of the pipe) due to the diameter reduction due to the fitting of the screw 2) Vertical processing finish of the shoulder surface 3) Thread taper angle difference between the pin 206 and the coupling 204 4) Above 2 ) And 3) difference between A pin side and B pin side
- this contact method affects the basic performance of the following threaded joints.
- Yield torque in the process of tightening the pins 206 to both ends of the coupling 204, the plastic deformation of the shoulder surface that resists tightening progresses, and the relationship between the tightening torque and the tightening rotation speed becomes the starting point showing non-linearity.
- ii) Tightening and tightening performance (seizure does not occur up to the specified number of times even if the threaded joint 200 is repeatedly tightened and tightened with a torque set below the yield torque).
- Airtightness (after tightening the threaded joint 200, gas or water as a pressure medium does not leak from the joint even if a combined load of axial tension / compression, internal pressure, and external pressure is applied).
- the center of the coupling has a shoulder portion overhanging on the inner diameter side of the pipe, and is coupled with the outer peripheral surface of the nose portion of the pin.
- the shoulder portion of the pin and the shoulder portion of the coupling come into contact with each other and tighten to a predetermined torque.
- the shoulder portion of the coupling paired with the shoulder portion of the pin is a machined surface, and a contact state with relatively little variation can be obtained.
- the premium joint having the above structure requires extremely high dimensional accuracy for each member, which increases the manufacturing cost.
- the screw interference amount of the premium joint shown in Patent Document 3 is controlled to be less than half the dimension of the API BTC screw of Non-Patent Document 1.
- the screw interference amount on the factory tightening side is set to the on-site tightening side in order to prevent the screw joint on the factory tightening side from turning around when tightening on site.
- the feature is that the tightening torque can be set higher than that on the on-site tightening side by making it larger than the screw interference amount in advance, and the effect of the contact surface on the threaded joint performance is not focused on.
- the present invention has been made in view of the above-mentioned actual conditions, and is provided at the tip of a pin inserted from both ends of A and B in addition to a high tightening torque for a threaded joint in which the shoulder portions at the tip of the pin are in contact with each other.
- the contact surface is affected by the vertical workability of the shoulder part and the angle of the thread taper, the shoulder angle for avoiding excessive plastic deformation of the shoulder surface and maintaining and improving the performance of the threaded joint. It is an object of the present invention to provide a threaded joint in which the relationship between the thread taper angle and the thread taper angle is specified under suitable conditions, and a method for connecting the threaded joint.
- a pin provided with a male threaded male thread on the outer peripheral surface of the tip of the first steel pipe, and a female threaded thread screwed with the male thread on the inner peripheral surfaces of both ends of the second steel pipe. It is a threaded joint including a coupling provided with, and is configured so that the shoulder surfaces of the tips of the pins come into contact with each other when the male threads of the pins are screwed into the female threads at both ends of the coupling.
- the relationship between the shoulder angle parameter and the screw taper angle parameter for the coupling and the two pins inserted from both ends of the coupling is defined by the following equation (1).
- the pin which is screw-fitted to the coupling, is first tightened to one of the couplings.
- the position is controlled in the axial center of the coupling with a jig indicating the tightening stop position of the one pin inserted from the end side of the coupling, and then the one pin and the other pin are tightened by tightening the other pin.
- the shoulder is taken into consideration the difference in the thread taper angle between the two pins inserted into the coupling and the coupling. It shows a suitable range of shoulder angle parameters for the two pins that directly affect the abutment. Therefore, according to the present invention, stress concentration and plastic deformation are avoided due to strong contact due to uneven contact between the shoulder surfaces of the pins, which contributes to stabilization and improvement of the tightening torque performance and airtightness performance of the threaded joint. be able to.
- the present invention is not a special screw (premium joint), there is no long sealing portion and the cutting length and the processing time can be short, so that the cost competitiveness and versatility are high. Further, the present invention provides seizure resistance and airtightness to the shoulder portion, which has only the function of generating high torque, as compared with the conventional threaded joint in which the shoulder surfaces are in contact with each other as shown in FIG. 1B. It is possible to have both, and thus the tightening and tightening performance and the airtightness performance can be improved.
- FIG. 6 is a cross-sectional view showing still another example of a conventional threaded joint.
- It is a conceptual diagram for demonstrating the form of contact between shoulder portions, and shows the case where the shoulder surface of the B pin is relatively perpendicular to the shoulder surface of the A pin.
- It is a conceptual diagram for demonstrating the form of contact between shoulder portions, and shows the case where the shoulder surface of B pin is inclined to the negative side with respect to the shoulder surface of A pin.
- It is a conceptual diagram for demonstrating the form of contact between shoulder portions and shows the case where the shoulder surface of pin B is inclined to the positive side relatively with respect to the shoulder surface of pin A.
- the present inventors set the tightening torque to a torque as high as the yield torque or less, and then set the shoulder angle ⁇ of the pin tip and the pin. It has been found that it is effective to specify a suitable relationship between the screw taper angle ⁇ of the coupling screw.
- FIG. 4 shows the shoulder angle parameter ⁇
- FIGS. 5A and 5B show the screw taper angle parameter ⁇ .
- the shoulder angle is set to 0 ° when cut at a right angle, and the inclination of the shoulder surface that opens the space on the outer diameter side of the shoulder is positive (Positive), and the opposite is negative (Negative). As, it is expressed here. Since each of the two pins has a shoulder, if the shoulder angle of the pin on the A end side (referred to as the A pin for convenience) is ⁇ A and the shoulder angle of the pin on the B end side (referred to as the B pin for convenience) is ⁇ B, the shoulder is shouldered.
- the screw taper angle difference will be explained.
- the thread taper a design value indicating the gradient is set, but in actual manufacturing, the thread taper has a tolerance range. If there is an angle difference between the thread taper of the pin and the coupling, the coupling generally has an outer diameter larger than the outer diameter of the pipe body and a pipe thickness thicker than the pipe body pipe thickness, so that the rigidity is high and the coupling screw. Forced to tilt along the tapered surface.
- the pin and the coupling generally have the same value as a taper screw.
- the API BTC screw of Non-Patent Document 1 has a taper of 1/16.
- the 1/16 taper represents an inclination in which the diameter decreases by 0.0625 inch in the radial direction when traveling 1 inch in the axial direction, which is 3.5763 ° when converted into an angle.
- the reason for considering the difference in thread taper angle is that the taper screw fits in the pin and the coupling during the tightening process, and the pin advances in the direction of the pipe axis in the coupling, but the rigidity of the coupling is higher than that of the pin. This is because the shoulder surface, which is the end surface of the pin installed in front of the threaded portion, is forcibly tilted along the taper of the coupling thread surface by the amount of the angle difference of the pin screw taper.
- the shoulder portion at the tip of the pin faces downward due to the diameter reduction of the pin as shown in FIGS. Even if the shoulder surface at the tip of the pin is manufactured vertically as designed, it will bend toward the inner surface of the pipe), and when the shoulder surfaces of the pins come into contact with each other, contact will start from the outer diameter side of the shoulder surface and gradually. The inner diameter side of the shoulder comes into contact with the shoulder.
- FIGS. 7A and 7B the tightening torque and the tightening rotation when the A pin is first screwed to the center of the A end side of the coupling to the center in the axial direction of the coupling and then the B pin is fitted from the B end side. Show the relationship between numbers.
- the position indicated by the arrow in the figure represents the yield torque of each case (the starting point where the plastic deformation of the shoulder surface progresses and the relationship between the tightening torque and the tightening rotation speed indicates non-linearity).
- FIGS. 8A to 8C show the axial stress distribution in the region near the shoulder when the B pin reaches the reference position CL (a position symmetrical with respect to the center of the coupling) of each case.
- the shoulder angle parameter ⁇ 0 ° as the initial value
- the shoulder bends downward (on the inner surface side of the pipe) due to the diameter reduction due to the fitting of the screw, so that a slight strong contact is made to the outer diameter side of the shoulder.
- the contact is made over the entire shoulder surface.
- FIG. 9 shows the contact pressure distribution of the shoulder surface at the yield torque of each case.
- the shoulder angle parameter is negative as in case 1
- the yield torque is such that the outer diameter of the shoulder comes into contact in advance and there is also deflection toward the inner diameter side of the pipe due to screw interference.
- Plastic deformation progresses with the movement toward the A pin side, and as shown in FIG. 7B, it is lower than that of Case 0 and Case 2.
- This method of contact is the basic performance of threaded joints: (i) Yield torque (in the process of tightening pins at both ends of the coupling, the plastic deformation of the shoulder surface that resists tightening progresses, and the tightening torque and tightening The torque at which the relationship between the number of revolutions is the starting point indicating non-linearity), (ii) Tightening and tightening performance (even if the threaded joint is repeatedly tightened and tightened with the specified torque, seizure does not occur up to the specified number of times), ( iii) The present invention affects the airtightness (gas and water as a pressure medium do not leak from the joint even when a combined load of axial tension / compression, internal pressure, and external pressure is applied after tightening the threaded joint).
- the threaded joint is tightened with a high tightening torque, a high contact pressure is generated on the shoulder contact surface, and the airtightness is improved.
- the high contact pressure on the contact surface and the bias of the contact pressure distribution cause local plastic deformation and increase the risk of seizure between metals due to the tightening and tightening of the threaded joint.
- the contact pressure on the shoulder contact surface is low, so the risk of seizure between metals during tightening and tightening of the threaded joint is low.
- the contact pressure of the shoulder contact surface is low, the airtight state cannot be maintained due to the pressure of the internal fluid acting on the threaded joint itself or the combined load of the pressure and the axial tensile load.
- the seizure resistance and the airtightness have contradictory properties, and it is further important to make the contact state of the contact surface suitable.
- the threaded joint 1 according to the embodiment of the present invention described below is based on the above-mentioned ideas, means, and methods.
- FIG. 10 shows the threaded joint 1 according to the embodiment of the present invention.
- the threaded joint 1 is a pin 3 provided with a male thread 2 which is a male tapered screw on the outer peripheral surface of the tip of the first steel pipe, and a female screwed with the male screw 2 on the inner peripheral surfaces of both ends of the second steel pipe.
- a coupling 5 provided with a female thread 4 which is a taper thread.
- the threaded joint 1 is configured so that the shoulder surfaces 6 at the tips of the pins 3 come into contact with each other when the male threads 2 of the pins 3 are screwed into the female threads 4 at both ends of the coupling 5.
- this embodiment Similar to the API BTC screw (hereinafter, also referred to as the prior art) of Non-Patent Document 1, this embodiment also has a screw taper of 1/16 in design.
- the 1/16 taper represents an inclination in which the diameter decreases by 0.0625 inch in the radial direction when traveling 1 inch in the axial direction, which is 3.5763 ° when converted into an angle.
- tolerances are set for the thread taper.
- the thread taper tolerance is 0.0610inch / inch to 0.066inch / inch (3.4907 ° to 3.77 °) for pin threads (male thread 2) and cups.
- the ring screw (female screw 4) is 0.060 inch / inch to 0.067 inch / inch (3.4336 ° to 3.8330 °).
- the aim of the screw taper is 0.0625 inch / inch (3.5763 °) for both the pin 3 and the coupling 5.
- the coupling 5 When there is an angle difference in the screw taper, the coupling 5 generally has a pipe thickness larger than the pipe body outer diameter and a pipe thickness larger than the pipe body pipe thickness, so that the coupling 5 has high rigidity, and the screw taper of the pin 3 is a cup.
- An angle change occurs along the thread taper surface of the ring 5 by the amount of the angle difference.
- the shoulder part at the tip of the pin screw corresponds to the difference of 0.006 inch. 0.17 ° Shoulder surface tilts to the positive side.
- the shoulder part at the tip of the pin screw corresponds to the difference of 0.006 inch. 0.17 ° Shoulder surface 6 will be tilted to the negative side.
- the inclination of the screw taper of the pin 3 is made shallow and the inclination of the screw taper of the coupling 5 is made deep, so that the inclination of the screw taper of the pin 3 is made deep.
- a difference was intentionally made in the aim of the taper to weaken the contact.
- the pin screw of this embodiment has a screw taper aim of 0.062 inch / inch (3.5478 °), the tolerance range is 0.0610 inch / inch to 0.066 inch / inch (3.4907 ° to 3.77 °), and the coupling screw has a screw taper aim of 0.064 inch.
- the taper is / inch (3.6619 °) with a narrow tolerance of 0.063inch / inch to 0.066inch / inch (3.6049 ° to 3.7760 °).
- SSC sulfuride stress corrosion cracking
- the screw taper angle parameter ⁇ affects the shoulder angle in the range of ⁇ 0.17 ° ⁇ ⁇ + 0.29 ° in the combination of the screw taper.
- the shoulder surface 6 of the A pin and the B pin was blasted, and the surface roughness was set to 63 to 190 ⁇ inch (1.6 to 4.8 ⁇ m) in Ra. That is, the surface roughness Ra of the shoulder surface 6 is 63 ⁇ inch (1.6 ⁇ m) ⁇ Ra ⁇ 190 ⁇ inch (4.8 ⁇ m).
- the lubricant was thinly and evenly applied not only to the screw portions but also to the blasted shoulder surface 6.
- FIG. 11 shows a comparison between the conventional technique shown in FIG. 1A and the screw interference amount of the present embodiment. Due to the fitting of the pin threaded portion and the threaded portion of the coupling 5, the surface pressure at the contact surface is proportional to the amount of screw interference from the shrink fitting type (Shrink Fit theory). Further, if the surface pressure is regarded as an evenly distributed load W generated over the threaded portion, and if the pin cross section is linearly approximated as a cantilever as shown in FIGS. 6A and 6B, the deflection is proportional to the amount of screw interference. It can be seen that the downward deflection (on the inner surface side of the pipe) of the pin tip is, after all, proportional to the amount of screw interference due to the diameter reduction accompanying the fitting of the screw.
- the amount of screw interference is smaller than that of the prior art, and the value thereof is the same as the screw representative diameter of the pin (same as the screw diameter E7 at the L7 position of the prior art screw.
- Non-Patent Document 1 The value divided by ( Figure 1, page 11 of Figure 1) was set to 0.0045, and the screw interference ratio between the pin and the coupling screw, that is, the screw fitting ratio, was kept constant regardless of the outer diameter size of the pipe body. That is, in the present embodiment, the design value of the screw fitting ratio is 0.0045, and the actual screw fitting ratio is 0.0032 or more and 0.0059 or less from the tolerance of the screw interference amount (+/- 0.006 ′′).
- the dimensions of the screws of the present application indicate the dimensions after threading, which shall be measured and confirmed before tightening.
- the relationship between the shoulder angle parameter ⁇ and the screw taper angle parameter ⁇ is more preferably defined by the following equation (3). That is, it is more reliable to adjust ⁇ on the plus (positive) side.
- the yield torque can be set higher as shown in FIGS. 7A and 7B. 0 ° ⁇ 2.0 ° ⁇ ⁇ ⁇ Equation (3)
- T Yield torque [ft-lbf]
- TS Shouldering torque [inch-lbf]
- D Delta torque [inch-lbf]
- P c Contact pressure in the threads [psi]
- E 7 Thread pitch Dia.
- L 4 Thread length [inch]
- w Coupling OD [inch]
- d Pipe inner diameter / Pipe ID [inch]
- D bv Bevel diameter / Bevel Dia.
- ⁇ m Thread interference on dia.
- the evaluation value of the yield torque is 23,410 ft-lbf (31,740 Nm).
- the actual value in the yield torque test conducted on the threaded joint 1 of the actual pipe is 28,000 ft-lbf (37,960 Nm) or more, which enables a safe and practical evaluation.
- the maximum tightening torque is 19,890 ft-lbf (26,970 Nm), which is 85% of the yield torque obtained by the evaluation formula, for the threaded joint 1 having the specifications shown in Table 2.
- the maximum tightening torque of the API BTC screw of Non-Patent Document 1 with the same diameter and thickness is 4,700 ft-lbf (6,370 N-m), and the tightening torque of the shoulder contact type screw joint 1 is not. It can be seen that it can be tightened with a higher torque than the contact type threaded joint.
- FIG. 12 shows the threaded joint 1 of the present embodiment so that the axial position of the A pin after tightening does not reach or exceed the axial center of the coupling 5.
- the jig 7 serving as a stopper is inserted in advance from the end face of the coupling 5 on the B end side on the opposite side, so that the shoulder at the tip of the A pin is shouldered. It is preferable to use a position adjusting jig 7 capable of appropriately arranging the surface 6 in the center of the inner surface of the coupling.
- the A pin is tightened in advance by position control, so that the shoulder surface 6 of the A pin and the B pin come into contact as intended at the center of the inner surface of the coupling even if there are various variations. Can be done.
- Table 2 shows the specifications of the pipe and coupling used in the screw test.
- Table 3 shows the shoulder angles ⁇ A and ⁇ B of the A pin and the B pin and the screw taper angle ⁇ PA, ⁇ PB, and the screw taper on the A end side and the B end side of the coupling 5
- the angles ⁇ CA and ⁇ CB were measured, and the following performance was evaluated using these test pieces.
- the design value of the screw fitting ratio was 0.0045, and the actual screw fitting ratio of the test piece was 0.0032 to 0.0059 due to the tolerance of the screw interference amount (+/- 0.006 ”). As shown in Fig.
- the design value of the screw fitting ratio differs depending on the outer diameter, and the tolerance of the screw interference amount (+0.006 ”/ -0.010”) is wide, so the actual screw fitting ratio is 0.0036 to 0.0083.
- the surface roughness Ra of the shoulder surface was set to 63 to 190 ⁇ inch (1.6 to 4.8 ⁇ m).
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Non-Disconnectible Joints And Screw-Threaded Joints (AREA)
- Earth Drilling (AREA)
- Mutual Connection Of Rods And Tubes (AREA)
Abstract
Description
1)ねじの嵌合に伴う縮径によって、ピン先端の下向き(管内面側)へのたわみ
2)ショルダー面の垂直加工仕上げ度
3)ピン206とカップリング204のねじテーパー角度差
4)上記2)と3)のAピン側とBピン側との差異
i)イールドトルク(カップリング204の両端にピン206を締付けていく過程で、締付けに抵抗するショルダー面の塑性変形が進み、締付けトルクと締付け回転数の関係が非線形性を示す開始点となるトルク)
ii)締付け締戻し性能(イールドトルク以下に設定したトルクで、ねじ継手200を繰返し締付け締戻ししても所定の回数まで焼付きが生じない)
iii)気密性能(ねじ継手200を締付けた後に、軸方向引張・圧縮、内圧、外圧の複合荷重を負荷しても圧力媒体となるガスや水が継手から漏れない)
カップリングと前記カップリングの両端から挿入された2つのピンについてのショルダー角度パラメータとねじテーパー角度パラメータの関係が下記式(1)で定義され、
下記式(2)で求められるイールドトルクの60%以上85%以下の締付けトルクで締付けられるねじ継手。
-1.5°≦Δθ―Δω≦2.0° ・・・式(1)
Δθ:2つのピンの締付け前のショルダー角度θA、θBの和で構成するショルダー角度パラメータ(Δθ=θA+θB)
Δω:カップリングと2つのピンの締付け前のねじテーパー角度差ΔωA、ΔωBの和で構成するねじテーパー角度パラメータ(Δω=ΔωA+ΔωB)
TS:ショルダリングトルク[inch-lbf]
TD:デルタトルク[inch-lbf]
Pc:ねじ接触圧[psi]
ft:ねじ摩擦係数(=0.035)
fs:ねじ摩擦係数(=0.080)
E7:ねじピッチ径[inch]
L4:ねじ長[inch]
w:カップリング外径[inch]
d:パイプ内径[inch]
Dbv:ベベル径[inch]
P:ねじリード(=1/TPI)[inch]
ρm:ねじ干渉量[inch]
As:ショルダー断面積(=π(Dbv 2-d2)/4)[inch2]
Rt:平均ねじ半径(=E7/2)[inch]
Rs:平均ショルダー半径(=(Dbv+d)/4)
Θ:ねじフランク角[deg.]
E:ヤング率[psi]
Ym:材料の降伏応力[psi]
0°<Δθ―Δω≦2.0° ・・・式(3)
ケース0:ショルダー角度パラメータΔθ=0°
ケース1:ショルダー角度パラメータΔθ=-2°
ケース2:ショルダー角度パラメータΔθ=+2°
本実施形態も非特許文献1のAPIBTCねじ(以下、従来技術とも呼ぶ)と同様に、設計上は1/16のねじテーパーを有している。1/16テーパーとは、軸方向に1inch進むと、径方向に0.0625inchだけ直径が小さくなる傾きを表しており、角度に換算すると3.5763°である。現実の製造ではねじテーパーに公差が設定されており、例えばAPIBTCねじでは、ねじテーパーの公差は、ピンねじ(雄ねじ2)は0.0610inch/inch~0.066inch/inch(3.4907°~3.776°)、カップリングねじ(雌ねじ4)は0.060inch/inch~0.067inch/inch(3.4336°~3.8330°)としている。なお、APIBTCねじの場合、ねじテーパーの狙いはピン3とカップリング5ともに0.0625inch/inch(3.5763°)となっている。
本実施形態のねじ継手1は、ピン3同士が当接する形式なので、ピン先端のショルダー角度の設定は、直接的に接触状態に影響を及ぼす。ショルダー角度の設定は、図4に示すように、直角に切削加工された場合を0°とし、ショルダー外径側に空間が開くショルダー面の傾きを“正”、その反対を“負”として、ここでは表現する。2つのピン3のそれぞれにショルダー部があるので、Aピンのショルダー角度をθA、Bピンのショルダー角度をθBとすると、ショルダー角度パラメータΔθはΔθ=θA+θBとなる。
-1.5°≦Δθ―Δω≦2.0° ・・・式(1)
ピン先端のショルダー面6の当接の状態に影響を与える因子として、既述の図6A、Bに示すように、ねじの嵌合に伴う縮径によって、ピン先端の下向き(管内面側)へのたわみがある。図11に、図1Aに示す従来技術と本実施形態のねじ干渉量を比較して示す。ピンねじ部とカップリング5のねじ部の嵌合により、その接触面での面圧は焼嵌め式(Shrink Fit理論)からねじ干渉量に比例する。また、その面圧をねじ部にわたって発生する等分布荷重Wとみなせば、図6A、Bに示すようにピン断面を片持ち梁として一次近似すると、たわみはねじ干渉量に比例する。ねじの嵌合に伴う縮径によって、ピン先端の下向き(管内面側)のたわみは、結局、ねじ干渉量に比例することが分かる。
0°<Δθ―Δω≦2.0° ・・・式(3)
カップリング5の両端からねじ接続されるピン3同士がカップリング5の軸方向の中央で当接する形式の鋼管用のねじ継手1のイールドトルクについて、本発明者らは、調査、実験の結果、非特許文献2のAPI7G Recommended Practice for Drill Stem Design and Operating Limits のAPPENDIX-Aに示される以下の式の変数をピン当接形式のねじ継手1にも適用することで安全側に評価出来ることを見出した。
T:イールドトルク/Yield torque[ft-lbf]
TS:ショルダリングトルク/Shouldering torque[inch-lbf]
TD:デルタトルク/Delta torque[inch-lbf]
Pc:ねじ接触圧/Contact pressure in the threads[psi]
ft:ねじ摩擦係数/Friction coefficient of threads(=0.035)
fs:ねじ摩擦係数/Friction coefficient of threads(=0.080)
E7:ねじピッチ径/Thread pitch Dia.[inch]
L4:ねじ長/Thread length[inch]
w:カップリング外径/Coupling OD[inch]
d:パイプ内径/Pipe ID[inch]
Dbv:ベベル径/Bevel Dia.[inch]
P:ねじリード/Lead of thread(=1/TPI)[inch]
ρm:ねじ干渉量/Thread interference on dia.[inch]
As:ショルダー断面積/Shoulder cross section(=π(Dbv 2-d2)/4)[inch2]
Rt:平均ねじ半径/Average mean thread radius(=E7/2)[inch]
Rs:平均ショルダー半径/Mean shoulder radius(=(Dbv+d)/4)
Θ:ねじフランク角/Thread flank angle[deg.]
E:ヤング率/Young's modulus[psi]
Ym:材料の降伏応力/Material yield stress[psi]
カップリング5の両端からねじ嵌合によって挿入されるピン3のショルダー面6同士の接触状態が、本実施形態のねじ継手1の性能に重要であるので、ピン3とカップリング5の締付けには留意が必要である。ねじ継手1の締付けに際しては、ピン3とカップリング5の両方のねじ表面とショルダー面6あるいはどちらか一方のねじ表面とショルダー面6に潤滑剤を均等に塗布して、金属同士の直接の接触とならないように締付けを行う。しかしながら、潤滑剤の個体差による摩擦係数の差異、締付け機械のパイプとカップリング5の掴む位置、公差範囲内ではあっても各ねじデザイン要素のばらつきなどによって、締付けトルクが同じであっても、カップリング5内に収まるピン3の軸方向位置がカップリング5の軸方向の中央(Center Line)からずれる可能性がある。
ねじ部およびショルダー部に、潤滑剤を塗布し、継手の締付け締戻し試験を最大10回繰返し行った。各回の締戻し後にねじ部とショルダー部の焼付きの有無を確認した。各回の締付けトルクは、表2、表3の諸元で58段落で説明した締付けトルク19,890 ft-lbf(26,970 N-m)を最大、締付けトルク14,050 ft-lbf(19,050 N-m)を最小の合格範囲として各回の締付けを行った。つまり、式(2)で求められるイールドトルクの60%以上85%以下の締付けトルクで各回の締付けを行った。繰返し締付け締戻し試験を10回問題なく完了した試験体について、次の気密試験を実施した。
繰返し締付け締戻し試験後の試験体を再度締付けて、ISO13679:2002年版のCAL2のシリーズB気密試験を行った。最大引張はAPI5CTのP110規格の最小降伏応力の95%に相当する荷重、最大圧縮は60%に相当する荷重を試験体に負荷した。気密試験は、ISO13679:2002年版に示す各荷重点で定められた軸力と圧力を負荷して、内部からの漏れの有無を確認しつつ実行した。表4に繰返し締付け締戻し試験と気密試験の結果を合わせて示す。比較例では繰返し締付け締戻し試験で焼付きが発生しているが、式(1)に適合する本発明例に係る試験体はいずれも繰返し締付け締戻し試験と気密試験の両方で合格している。
なお、別途実施したFEAの結果においても、図13に示すように、ショルダー角度パラメータΔθとねじテーパー角度パラメータΔωの関係が式(1)を満たす場合に、ショルダー面での最大接触圧が顕著に低下していることが確認されている。つまり、図13に示す結果は、ショルダー角度パラメータとねじテーパー角度パラメータを好適範囲に設定することが、耐焼付き性の向上に寄与する最大接触圧(と最大接触圧が生じる部分の周辺の接触圧分布)の低減に効果的であることを示している。また、上記実験ではパイプ外径5.5inchのものを使用したが、4.5~7inchのものでも同様の結果が得られることが確認されている。
2 雄ねじ
3 ピン
4 雌ねじ
5 カップリング
6 ショルダー面
7 治具
Claims (5)
- 第1の鋼管の先端の外周面に雄のテーパーねじである雄ねじが設けられたピンと、第2の鋼管の両端の内周面に前記雄ねじと螺合する雌のテーパーねじである雌ねじが設けられたカップリングとを含むねじ継手であって、前記カップリングの両端の雌ねじのそれぞれに前記ピンの雄ねじを螺合させた際に、前記ピンの先端のショルダー面同士が接触するよう構成されたねじ継手において、
カップリングと前記カップリングの両端から挿入された2つのピンについてのショルダー角度パラメータとねじテーパー角度パラメータの関係が下記式(1)で定義され、
下記式(2)で求められるイールドトルクの60%以上85%以下の締付けトルクで締付けられるねじ継手。
-1.5°≦Δθ―Δω≦2.0° ・・・式(1)
Δθ:2つのピンの締付け前のショルダー角度θA、θBの和で構成するショルダー角度パラメータ(Δθ=θA+θB)
Δω:カップリングと2つのピンの締付け前のねじテーパー角度差ΔωA、ΔωBの和で構成するねじテーパー角度パラメータ(Δω=ΔωA+ΔωB)
TS:ショルダリングトルク[inch-lbf]
TD:デルタトルク[inch-lbf]
Pc:ねじ接触圧[psi]
ft:ねじ摩擦係数(=0.035)
fs:ねじ摩擦係数(=0.080)
E7:ねじピッチ径[inch]
L4:ねじ長[inch]
w:カップリング外径[inch]
d:パイプ内径[inch]
Dbv:ベベル径[inch]
P:ねじリード(=1/TPI)[inch]
ρm:ねじ干渉量[inch]
As:ショルダー断面積(=π(Dbv 2-d2)/4)[inch2]
Rt:平均ねじ半径(=E7/2)[inch]
Rs:平均ショルダー半径(=(Dbv+d)/4)
Θ:ねじフランク角[deg.]
E:ヤング率[psi]
Ym:材料の降伏応力[psi] - 前記関係が下記式(3)で定義される、請求項1に記載のねじ継手。
0°<Δθ―Δω≦2.0° ・・・式(3) - ショルダー角度パラメータΔθが、-1.21°≦Δθ≦1.83°である、請求項1または2に記載のねじ継手。
- ねじ嵌合比が0.0032以上0.0059以下である、請求項1~3のいずれか1項に記載のねじ継手。
- 請求項1~4のいずれか1項に記載のねじ継手を接続するために、先に前記カップリングとねじ嵌合する一方の前記ピンの締付けを、前記カップリングの一方の端側から挿入した前記一方のピンの締付け停止位置を示す治具で前記カップリングの軸方向中央に位置制御して、その後、他方の前記ピンの締付けで前記一方のピンと前記他方のピンのショルダー面同士を当接する、ねじ継手の接続方法。
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BR112023005702A BR112023005702A2 (pt) | 2020-09-30 | 2020-09-30 | Junta roscada de tubo e método de conexão para a mesma |
US18/044,990 US20230383875A1 (en) | 2020-09-30 | 2020-09-30 | Threaded joint of pipe and method for connecting same |
JP2021528462A JP7248117B2 (ja) | 2020-09-30 | 2020-09-30 | 管のねじ継手およびその接続方法 |
CA3190633A CA3190633A1 (en) | 2020-09-30 | 2020-09-30 | Threaded joint of pipe and method for connecting same |
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Citations (3)
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JP2003512588A (ja) * | 1999-10-21 | 2003-04-02 | バローレック・マネスマン・オイル・アンド・ガス・フランス | 外圧に耐えるねじ付パイプコネクタ |
JP2012067908A (ja) * | 2010-08-27 | 2012-04-05 | Jfe Steel Corp | 鋼管用ねじ継手 |
WO2018003455A1 (ja) * | 2016-06-30 | 2018-01-04 | 新日鐵住金株式会社 | 管用ねじ継手及び管用ねじ継手の製造方法 |
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US6817633B2 (en) * | 2002-12-20 | 2004-11-16 | Lone Star Steel Company | Tubular members and threaded connections for casing drilling and method |
JP2006189089A (ja) * | 2005-01-06 | 2006-07-20 | Mitsubishi Plastics Ind Ltd | 配管接合用標線記入治具及び配管の接合方法 |
JP2009243613A (ja) * | 2008-03-31 | 2009-10-22 | Sanki Eng Co Ltd | 管体や継手の接続方法、及び管体接続用マーキングゲージ |
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JP2003512588A (ja) * | 1999-10-21 | 2003-04-02 | バローレック・マネスマン・オイル・アンド・ガス・フランス | 外圧に耐えるねじ付パイプコネクタ |
JP2012067908A (ja) * | 2010-08-27 | 2012-04-05 | Jfe Steel Corp | 鋼管用ねじ継手 |
WO2018003455A1 (ja) * | 2016-06-30 | 2018-01-04 | 新日鐵住金株式会社 | 管用ねじ継手及び管用ねじ継手の製造方法 |
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