JP5812266B2 - Manufacturing method of threaded joint for steel pipe - Google Patents

Description

  TECHNICAL FIELD The present invention relates to a threaded joint for steel pipes, and in particular, oil well pipes including tubing and casings generally used for exploration and production of oil wells and gas wells, that is, OCTG (oil country tubular goods), riser pipes, line pipes, etc. The present invention relates to a threaded joint for steel pipes that is suitable for use in connecting steel pipes and has excellent sealing properties and compression resistance.

  Threaded joints are widely used to connect steel pipes used in oil industry equipment such as oil well pipes. Conventionally, a standard threaded joint specified in the API (American Petroleum Institute) standard has been typically used for connecting steel pipes used for oil and gas exploration and production. However, in recent years, the wells for crude oil and natural gas have been deepened, and the number of vertical wells, horizontal wells, inclined wells, etc. has increased, and the drilling and production environment has become severe. In addition, the demand for screw joints such as compression resistance, bending resistance, and external pressure seal performance (external pressure resistance) has diversified due to the increased development of wells in poor environments such as the ocean and polar regions. ing. For this reason, the use of high-performance special threaded joints called premium joints is increasing, and the demands on the performance are also increasing.

  A premium joint usually has a male screw member (hereinafter referred to as a pin) formed on a pipe end portion, each having a taper screw, a seal portion (specifically, a metal touch seal portion), and a shoulder portion (specifically, a torque shoulder portion). It is a coupling type joint in which a female screw member (hereinafter referred to as a box) for connecting pins to each other is coupled. The taper screw is important for firmly fixing the pipe joint, and the seal part plays a role of securing the sealing performance by metal contact between the box and the pin at this part, and the shoulder part is a stopper of the joint during tightening. It becomes the shoulder side that plays the role.

  FIG. 3 is a schematic vertical sectional view of a threaded joint of a circular pipe as an explanatory diagram of a premium joint for oil well pipes, (a) is an overall view, (b) is an enlarged view showing a threaded portion in (a), c) is an enlarged view showing the vicinity of the pin nose in (a). The threaded joint includes a pin 3 and a box 1 corresponding to the pin 3, and the pin 3 has a male screw portion 7 on the outer surface thereof and a screwless portion provided adjacent to the male screw portion 7 on the distal end side of the pin 3. It has a nose portion 8 (pin nose 8) which is a length portion. The nose portion 8 has a seal portion 11 on its outer peripheral surface and a torque shoulder portion 12 on its end surface. The opposing box 1 has a female screw part 5, a seal part 13, a part that can be screwed or contacted with the male screw part 7, the seal part 11, and the shoulder part 12 of the pin 3 on the inner surface thereof, respectively. A shoulder portion 14 is provided.

  On the other hand, as a proposal of a threaded joint particularly resistant to external pressure load, for example, Patent Document 1 discloses a radial seal type in which a nose portion on a pin tip side is in metal-metal contact with a box inner surface in a radial direction and the contact portion becomes a seal portion. In the threaded joint, a pin nose portion having discontinuity with the seal portion (discontinuity that the outer surface of the nose portion is radially outward from the extension line of the seal surface) is provided between the seal portion and the shoulder portion, A method is disclosed in which this part is not in contact with the box. In this method, by providing the seal portion at a location away from the tip of the pin, high airtightness can be obtained even when the pin is relatively thin.

Japanese Patent No. 4535064

  However, in the method of Patent Document 1, since the discontinuity with the seal portion is imparted to the pin nose portion, there is a problem that the shape becomes complicated and the processing efficiency is sacrificed.

In order to solve the above problems, the inventors have repeatedly studied by simulation calculation and experiment by FEA (finite element analysis), and as a result, limit the seal point defined by a specific mathematical expression to a specific range. Thus, the present invention was made by obtaining the knowledge that a screw joint having a simple pin nose shape but having high airtightness even in an external pressure environment can be obtained.
That is, the present invention is as follows.
(1)
A pin having a male screw part, a nose part extending from the male screw part to the tube end side, and a shoulder part provided at the tip of the nose part;
A female screw part that is screw-coupled with the male screw part to form a screw part, a seal surface that faces the outer peripheral surface of the nose part of the pin, and a box that has a shoulder part that contacts the shoulder part of the pin, wherein the pin and the nose portion outer peripheral surface of the box and is coupled pin and the sealing surface of the box metal by means of a screw coupling - to the contact portion and the metal contact name a sealing portion,
Nose outer peripheral surface of the pin is a single tapered sealing surface of the box A method of manufacturing a threaded joint for curved der Ru steel tube outwardly convex,
Regarding the sealing surface of the box,
Calculating a sheet Lumpur point _{x p} by the formula shown in Equation 1, the production of a threaded joint for steel pipes the calculated value issued to said <br/> that the sealing surface shape which is less than 5.08 mm 25.4 mm Way .

  ADVANTAGE OF THE INVENTION According to this invention, the screw joint for steel pipes which has high airtightness also in an external pressure environment although it is a simple pin nose shape is obtained.

It is a longitudinal cross-sectional schematic diagram which shows one example of embodiment of this invention. It is a longitudinal cross-sectional schematic diagram which shows one example of embodiment of this invention. It is a longitudinal cross-sectional schematic diagram which shows the conventional threaded joint for steel pipes.

  As shown in FIGS. 1 and 2, the threaded joint for steel pipes according to the present invention is provided with a male screw part 7, a nose part 8 extending from the male screw part 7 to the pipe end side, and a tip of the nose part 8. A pin 3 having a shoulder portion 12 formed therein, a female screw portion 5 screwed to the male screw portion 7 to form a screw portion, a seal surface 21 facing the outer peripheral surface of the nose portion of the pin 3, and the pin 3 A box 1 having a shoulder portion 14 abutting against the shoulder portion 12, and the pin 3 and the box 1 are coupled by the screw coupling so that the outer peripheral surface of the nose portion of the pin 3 and the seal surface 21 of the box 1 are It was assumed that this was a steel pipe threaded joint with metal-metal contact and the contact part forming the seal part 20 (a threaded joint equivalent to a conventional radial seal type premium joint).

In the present invention, based on the above premise, as shown in FIG. 1, the outer peripheral surface of the nose portion of the pin 3 (pin nose outer peripheral surface 31) has a single tapered shape, and the sealing surface 21 of the box 1 has a curved surface shape that protrudes outward. targeting those is, with the number 1 in the indicated formula 0.2 inches sealing point x _p defined by (also described in FIG. 1) (0.2 inches × 25.4 mm / inch = 5.08 mm) or more It was decided to. FIG. 1 also shows a schematic distribution diagram of p with respect to x.

By the x _p and less than 0.2 inches, a real significant pins reduced outer diameter under external pressure environment, it can ensure high airtightness. Since the pin nose base gap 41, which is a gap that exists from the boundary of the seal portion 20 to the screw portion side to the tip of the screw portion, communicates with the outside through a screw gap that is a gap that exists in the screwed screw portion, Under an external pressure environment, an external pressure acts in the pin nose base clearance 41, and the external pressure 31 receives a pressing force by the external pressure. However, if x _p is less than 0.2 inch, the pin 3 resists the pressing force. The pin outer diameter is significantly reduced and the pin nose outer peripheral surface 31 and the seal surface 21 are in poor contact with each other, and airtightness cannot be secured.

However, increasing the x _p until greater as 1.0 inches, not necessarily lead to a further improvement in airtightness, lowering the machining productivity rather length of the nose portion including a sealing portion becomes unnecessarily long because only so that, x _p is preferably not more than about 1.0 inches.
In the calculation of the seal point x _p, x _1, x ₂ lower limit as the upper limit of the range of integration, so that the same size longitudinal sectional view of the pin 3 and the box 1 are the tubes axes and shoulder faces coincide with each other X-coordinates and identifications of the two intersections of the pin nose outer peripheral surface 31 and the seal surface 21 (the two intersection points correspond to the pin tip end point and the screw end point of the seal part 20), respectively, when they are superimposed Is done. Here, the x-axis is parallel to the tube axis direction, and the tip of the pin nose is the origin. That is, x is the distance in the tube axis direction from the tip of the pin nose. Further, the contact surface pressure p is obtained as a function of x from FEA calculation simulating LP2 in the ISO 13679 series A test. Here, in the same FEA calculation, the element size is assumed to be 0.001 to 0.01 inch, and the box and the pin are assumed to be elastic-plastic.

For threaded joints consisting of a pin formed by machining the end of a steel pipe with an outer diameter of 9 + 5/8 inch and a wall thickness of 0.545 inch and a box corresponding to this, a curved surface protruding outside the pin taper shape and / or box seal surface Samples with various shapes were produced. With respect to the sample, the seal point x _p was calculated by the equation shown in Equation 1 using the contact pressure p obtained by FEA calculation simulating LP2 in the ISO 13679 series A test. Moreover, the same A test was implemented about the sample. The results are shown in Table 1.

  As shown in Table 1, it is clear that the inventive examples have better sealing properties than the comparative examples.

1 box
3 pin
5 Female thread
7 Male thread
8 Nose (pin nose)
11,13,20 Seal (Details are metal touch seal)
12,14 Shoulder (For details, Torque shoulder)
21 Seal surface
31 Pin nose outer surface (pin nose outer surface)
41 Pin nose base clearance

Claims (1)

A pin having a male screw part, a nose part extending from the male screw part to the tube end side, and a shoulder part provided at the tip of the nose part;
A female screw part that is screw-coupled with the male screw part to form a screw part, a seal surface that faces the outer peripheral surface of the nose part of the pin, and a box that has a shoulder part that contacts the shoulder part of the pin, wherein the pin and the nose portion outer peripheral surface of the box and is coupled pin and the sealing surface of the box metal by means of a screw coupling - to the contact portion and the metal contact name a sealing portion,
Nose outer peripheral surface of the pin is a single tapered sealing surface of the box A method of manufacturing a threaded joint for curved der Ru steel tube outwardly convex,
Regarding the sealing surface of the box,
Calculating a sheet Lumpur point _{x p} by the formula shown in Equation 1, the production of a threaded joint for steel pipes the calculated value issued to said <br/> that the sealing surface shape which is less than 5.08 mm 25.4 mm Way .

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