CA1316964C - Tubular coupling with improved metal to metal seal - Google Patents
Tubular coupling with improved metal to metal sealInfo
- Publication number
- CA1316964C CA1316964C CA000445363A CA445363A CA1316964C CA 1316964 C CA1316964 C CA 1316964C CA 000445363 A CA000445363 A CA 000445363A CA 445363 A CA445363 A CA 445363A CA 1316964 C CA1316964 C CA 1316964C
- Authority
- CA
- Canada
- Prior art keywords
- pin
- shoulder
- box
- internal
- mating
- Prior art date
- Legal status (The legal status 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 status listed.)
- Expired - Lifetime
Links
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
- 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
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH DRILLING; MINING
- E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
- E21B17/02—Couplings; joints
- E21B17/04—Couplings; joints between rod or the like and bit or between rod and rod or the like
- E21B17/042—Threaded
- E21B17/0423—Threaded with plural threaded sections, e.g. with two-step threads
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH DRILLING; MINING
- E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
- E21B17/02—Couplings; joints
- E21B17/08—Casing joints
-
- 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
Abstract
TUBULAR COUPLING WITH IMPROVED
METAL TO METAL SEAL
ABSTRACT
Metal to-metal seals for pin and box member tubular joints are disclosed where mating annular surfaces are machined at slightly different angles such that the bearing load from initial contact is entirely on the leading edge of the pin annular surface and the trailing edge of the box annular surface. The mismatch of the sealing surfaces is selected for any particular seal geometry such that at final make-up, the bearing load has a relatively even distribution across the entire sealing surface in contact, thus broadly distributing make-up bearing stresses and minimizing any resulting tendency for galling that may occur, in particular for joints having relatively thick walls for both pin and box members.
METAL TO METAL SEAL
ABSTRACT
Metal to-metal seals for pin and box member tubular joints are disclosed where mating annular surfaces are machined at slightly different angles such that the bearing load from initial contact is entirely on the leading edge of the pin annular surface and the trailing edge of the box annular surface. The mismatch of the sealing surfaces is selected for any particular seal geometry such that at final make-up, the bearing load has a relatively even distribution across the entire sealing surface in contact, thus broadly distributing make-up bearing stresses and minimizing any resulting tendency for galling that may occur, in particular for joints having relatively thick walls for both pin and box members.
Description
- `
1316~64 ~ This invention relates generally to oil and gas well tubing and more particularly has to do with the construction of high pressure tubular joints operable when made up and run into a well to withstand extreme -~ S fluid pressures and for sealing off thereof to prevent escape of high pressure fluid or gas through the tubular assembly at the joints.
The search for oil and gas reserves has brought about the exploration of ever deeper formations. These ~10 deeper formations require longer strings of production ; pipe, casing, llners and drll} pipe used in the~explora- ~
tion and production o oil and gas. Such wells~may~be ~ _ sub~ect to~extremely high pressures from formation~
zones. ~The increased length of tubular strings imposes 15 the upper~portion of the string to very high tensile~
loads and~where~high pressure exists from deeper~forma-tions,~may also expose the upper portion of the~string to high internal pressures where there is~little or no off-setting external pressure on the tubing. With standard 0~ olnts there are limltation~s to~the~depths to whlch a string~of tubing can~be run.
There~have been prior art attempts to provide metal-to-metal seals which can withstand :the extreme prassures~that~the tubulàr joint~is required to with-25~ hold.
U.S. Patent No. 2,893,759~issued in the name of , .~ ' ' .
.
,.. ,;. ~
1 31 6~64 -- 2Thomas L. Blose, one of the inventors of the present in-vention, is entitled "Conically '~apered Screw-Type Casing Joint With Metal-To-Metal Seal". The patent discloses a metal to metal seal where a different sealing taper is 5 provided on the box and pin sealing surfaces to gen- I
erate an area of radial deformation of the sealing sur-faces upon make-up of the connection. The sealing sur-face of the pin is provided with a higher taper angle than that of the box sealing surface, so that upon joint 10 make-up a line contact is initially established between the sealing surfaces. Upon further make-up, at least one of the members is de~ormed radially to generate a sur-face contact between the sealing surfaces. Since the sealing of the pin has a higher taper or angle of in-15 cline with respect to the coaxial axis of the pin andbox, the trailing edge of the pin sealing surface is the first to contact the annular sealing surface of the box on initial make-up.
The conical and crown-type metal-to-metal seal-20 ing geometries in use today for high pressure joints for the oil and gas industry, typically have pin and box members machined to the same nominal angle of engage-ment as measured from the tubular axis. This angle is typically between two degrees t2) and fifteen degrees 25 (15), but may be of any angle. A typical conical seal of any given width would have both pin and box seals machined to a nominal fourteen degrees (14) for their entire widths. A crown-type seal of fourteen degrees (14) is disclosed in U.S. Patent No. 2,992,019 issued .
30 in the name of MacArthur where a crown seal is provide on the pin member and is machined at the same angle as the sealing surface on the box member.
It has been found that for parallel or near parallel mating surfaces such as sealing surfaces of ` 35 conical or crown-type metal-to-metal seals of the same or substantially the same angles, the bearing loads shift .
131696~
from the leading edge of the seal on initial contact to the trailing edge upon final make-up. Depending on the amount of radial interference induced, the leading seal edge can be depleted of all bearing load as the load is 5 transferred further and further bacX toward the trailing seal edge with the increase in metal-to-metal inter-ference. ~t very high levels of interference the trail-ing edge of the seal can receive bearing loads sufficient to cause not only unnecessarily high stress levels of 10 interfexence in the seal area, but even yielding of the material in a seal surface. This yielding or plastic metal surface distortion, sometimes also referred to as galling, can lead to the metal-to-metal seal losing its pressure containment ability. For this reason, the amount 15 of interference between sealing members has heretofore been limited to avoid attainment of the galling thre~h~l~.
This, however, has tended to lower the maximum pressure containment limit of typical metal-to metal seals, par-ticularly on thick wall, high yield strength tubular 20 goods.
The metal-to-metal seal described in U.S. Patent No. 2,893,759 mentioned above provides that the angle of incline of the sealing surface on the pin member be greater than the angle of incline of the sealing surface 25 on the box member. This arrangement necessarily causes the trailing edge of the pin sealing surface to first ; come in contact with the sealing surface on the box mem-ber and upon further make-up, at least one of the mem-bers is deformed radially whereby the bearing load on 30 the final seal is greatly distorted ~at a particular point, typically~the trailing edge of the seal.
It is therefore an object of this invention to provide a metal-to-metal seal in a tubular joint that has a substantiall~ uniform loading distribution 35 across the axial extent of the metal-to-metal contact between the male and female members.
.
, . .
fl// 1 3 1 6 9 6 ~-lr The present invention therefore provides a tubing joint comprising, tubular pin and box members for coaxial mating, the box member having a counterbore for receiving the pin member and having an annular inwardly facing internal shoulder inclining at an angle with respect to the axis of the box member, the pin member having a conical internal shoulder at its free end for coaxial mating with said box member annular shoulder, said pin member having a thick wall and a high yield strength in the vicinity of said internal pin shoulder, said internal pin shoulder inclining inwardly toward the end of the pin member, the angle of incline of said internal pin shoulder with respect to the pin axis being less than the box internal shoulder incline angle, whereby upon coaxial mating of said shoulders the bearing load distribution across said shoulders is approximately uniform, and mating threads on the box and pin members respectively spaced from said shoulder.s outwardly on the box member and outwardly on the pin member, said pin member having its internal shoulder formed on the exterior wall of a length of substantially solid cylindrical tubing, said tubing having a substantially smooth internal bore in the axial vicinity of said internal pin shoulder.
The present invention also provides a tubing joint comprising, tubular pin and box members for coaxial mating, the box member and having a counterbore for receiving the pin member and having an annular inwardly facing external shoulder inclining at an angle with respect to the axis of the box member, the pin member having a conical external shoulder at its fixed end for coaxial mating with said box member annular shoulder, said external pin shoulder inclining inwardly toward the free end of the pin member, the angle of incline of said external box shoulder with respect to the box axis being ~J
.
-4a- 1 31 6q64 -less than the pin external shoulder incline angle and, mating threads on the box and pin members respectively spaced from said shoulders inwardly on the box member and outwardly on the pin member.
Further features and advantages of this invention will be more readily understood from the following description of the preferred embodiments of the invention taken together with the accompanying drawings wherein:
Figure 1 is a longitudinal section of a fully made-up tubular joint embodying the principles of the invention with only part of the joint being shown, and the rest being broken away;
:: :
,.: . . .
.
" 1 31 696~
Figure 2 is a representation of conical sealing surfaces on the box and pin members;
Figure 3 is a representation of a crown-type seal on a pin member for sealing with a conical surface 5 on the box member;
Figure 4 represents a made-up sealing surface of ~:
a box and pin member and shows the stress distribtuion when the seal is fully made-up;
Figure 5 shows the bearing loads on a fully lO made-up sealing surface where the angles of incline are substantially the same for the box and pin members;
Figure 6 shows conical sealing surfaces ac-cording to the invention where the angle of incline of the pin sealing surface is less than that of the box 15 sealing surface;
Figure 7 shows a fully made-up seal between the box and pin members where the angle of incline of the pin member is less than that of the box member and ad-ditionally shows the stress distribution across the width 20 of the sealing surface;
Figure 8 shows a crown-type sealing surface on a pin member as it initially is being made up with a conical surfaced box member; and ` Figure 9 shows a fully made-up sealing surface 25 of crown-type surface on a pin member and conical box member and showing th~ stress distribution across the axial width of the sealing surface.
~ Figure l shows a typical tubing joint lO com-: prising box member 20 and pin member 30 with two step 30 threads 21 and 22. Tubing joint lO has an external seal 40 and an:internal seal 50 for sealing against external ~-and internal pressure differences caused by high pres-sure fluid and gas, either inside or external to the :tubing joint.
35 : Figure 2 illustrates a metal-to-metal seal in :: : ~
:
!
- 6 _ 1316~6~ :
use today in the oil and gas industryO These seals comprise members machined to the same nominal angle of engagement from the tubing axis. Figure 2 represents a conical metal-to-metal seal and may be used to rep-5 resent either an internal seal 50 or an external seal 40 as in Figure 1. For the case of an internal seal, element 70 represents the pin member while element 80 represents the box member. For the case of an external seal, element 80 represents the box memher (element 20 10 in Figure 1) while element 80 represents pin member (element 30 in Figure 1).
The angle ~f engagement as shown in Figure 2 for prior art metal-to-metal seals is usually between two degrees (2) and fifteen degrees (15) but may be of 15 any angle. For instance, a typical conical seal of a nominal fourteen degrees (14) of any given width would have both pïn and box seals machined to a nominal four-teen degrees tl4) for the entire widths.
Similarly, Figure 3 shows a metal-to-metal seal 20 wherein element 71 represents a crown-type seal where surface 72 is machined to be fourteen degrees (14) for engagement with a nominal fourteen degree (14) incline L
of element 81. As the description of Figure 2 indicated in a similar fashion, element 81 represents the box 25 member for an internal seal with element 71 being the pin member and vice versa for the external seal il-lustrated at 40 in Figure 1.
Figure 4 illustrates a conical-type seal, where elements 70 and 80 represent either pin and box 30 elements (depending upon whether the seal under review is an internal seal or an external seal) and where the ~-sealing surfaces 70' and 80' are machined to substantial-ly the~same angle. A stress distribution represent~tion is illustrated as a function of axial contact length be-35 low the contacting surfaces 70l and 80' when the sur-.
faces are fully made-up. Figure 4 illustrates that a higher stress levels in one area of the sealing surface, the trailing edge of the surface, may become extremely high. The leading and trailing edge as used herein are 5 measured with respect to the member having the least thickness of metal, that is with respect to the pin surface for an internal seal, the box surface for an external seal. If the stress level is extreme in one section of the seal, the metal-to-metal seal may become 10 subjec~ to premature galling and the surrounding geo-metry could become subject to increased incidence of stress induced preferential corosion or fatigue failure. Similarly, if the bearing load gets too high, the material could yield allowing the possible passage 15 of previously contained fluid or gas.
Figure 5 illustrates how the extreme high b~ar--ing loads on the seals having substantially equal in-clining surfaces can cause member 70 to rock about the trailing edge of the sealing surface and ultimately lead 20 to the problems discussed above.
Figure 6 shows a sealing surface according to the invention where the sealing surface 75 is machined at an angle A' with respect to its axis somewhat less than tha angle A of sealing surface 85 of element 80. As 25 discussed above if the sealing arrangement of Figure 6 is used as an internal seal, element 70 represents the pin member 30 and element 80 represents the box member 20. As the element 70, representing a pin member of an internal seal is initially made-up with the female 30 member or box member 80, it makes initial contact with box member 80 at cylindrical line 100. It is apparent that on initial mating, the bearing load is substantial-ly on the leadin~ edge of the pin shoulder with the trailing edge of the box shoulder.
a 1 31 696~
It should be apparent that Figure 6 also rep-resents ~he case for an external seal where element 70 represents the box member and element 80 represents the pin member. Where Figure 6 represents an internal 5 seal, element 70 representing the pin member is machined to be a lower taper or incline angle than that of the box member 80. Where Figure 6 represents an external seal, the box sealing surface 70 is machined to a smaller angle than that of the pin member 80.
Figure 7 shows the elements 70 and 80 in a fully made-up condition and indicates with a stress versus length diagram beneath the seal that the stress as a function of axial width is uniform and, in this case, a "U" shape.
Figure 8 represents a box element 81 and a pin element 71 for an internal seal in which the crown sur face 72 of element 71 is adapted for mating with conical surface 82 of element 81. According to the invention, the angle of incline of surface 72 of element 71 is 20 machined to be less than the~angle of incline of surface 82 of element 81 such that the leading edge of element 71 engages element 81 at the cylindrical line 76 about the conical surface. Figure 8 illustrates that the angle ;;
B' or the incline of the element 71 about the axis of -25 element 72 is less than the angle B which represents the angle of incline of sealing surface 82 of element 81.
Figure 9 shows the crown sealing surface 72 of element 71 in the fully made-up position and illustrates the stress distribution across the axial width of the ~
- ; 30 sealing surface. As illustrated, the stress distribution ~is uniform in width and is "U" shaped. As discussed ~with respect to Flgure 6 for the conical sealing sur-faces, the crown sealing surface represented in Figure 8 may be located at other regions of the tubular con-35 nection and used for either an internal seal, an external seal, or both an internal and an external seal. In this 9,, ': - .
' , ' . ' " ' '~
: ~
1 31 6q6~
g example, an internal seal element 81 would represent 3 the box member while element 71 would represent the pin member. Likewise, for an external seal as at 40 in Figure 1, element 81 would represent the pin member while 5 element 71 would represent the box memberO
According to the invention as illustrated in s;
the sealing arrangements of Figures 6 and 8, the exact mismatch of the sealing surfaces will vary depending on the seal angle of the more rigid member, the width of 10 the sealing surface, the thickness of the thinner member relative to its seal diameter, the thickness of the thinner member relative to the thickness of the thicker member at the seal region, desired tolerances, and other factors. For example, it can be shown that seal 15 mismatch for very low angle seals of approximately one-half inch (1/2") in axial width can be as low as one quarter degree (1/4), and high angle seals of equal axial width may require a mismatch of one degree (1) or more for complete balancing of bearing loads upon 20 full make-up~ Finite element analysis may be used as a tool to verify the optimum seal angle mismatch on any given seal and connection geometry.
The sealing surfaces according to the invention may be used either singularly as an internal seal, ~ -25 singularly as an external seal, or may be used together in a tubular connection having both an internal and ex-ternal seal.
From the foregoing, it is apparent that there has been provided a sealing surface for use in joints 30 interconnecting tubular members used in oil and gas ,~
wells. Various modifications and alterations in the described structures will be apparent to those s~illed in the art from the foregoing description which do not depart from the scope of the invention~
b~
1316~64 ~ This invention relates generally to oil and gas well tubing and more particularly has to do with the construction of high pressure tubular joints operable when made up and run into a well to withstand extreme -~ S fluid pressures and for sealing off thereof to prevent escape of high pressure fluid or gas through the tubular assembly at the joints.
The search for oil and gas reserves has brought about the exploration of ever deeper formations. These ~10 deeper formations require longer strings of production ; pipe, casing, llners and drll} pipe used in the~explora- ~
tion and production o oil and gas. Such wells~may~be ~ _ sub~ect to~extremely high pressures from formation~
zones. ~The increased length of tubular strings imposes 15 the upper~portion of the string to very high tensile~
loads and~where~high pressure exists from deeper~forma-tions,~may also expose the upper portion of the~string to high internal pressures where there is~little or no off-setting external pressure on the tubing. With standard 0~ olnts there are limltation~s to~the~depths to whlch a string~of tubing can~be run.
There~have been prior art attempts to provide metal-to-metal seals which can withstand :the extreme prassures~that~the tubulàr joint~is required to with-25~ hold.
U.S. Patent No. 2,893,759~issued in the name of , .~ ' ' .
.
,.. ,;. ~
1 31 6~64 -- 2Thomas L. Blose, one of the inventors of the present in-vention, is entitled "Conically '~apered Screw-Type Casing Joint With Metal-To-Metal Seal". The patent discloses a metal to metal seal where a different sealing taper is 5 provided on the box and pin sealing surfaces to gen- I
erate an area of radial deformation of the sealing sur-faces upon make-up of the connection. The sealing sur-face of the pin is provided with a higher taper angle than that of the box sealing surface, so that upon joint 10 make-up a line contact is initially established between the sealing surfaces. Upon further make-up, at least one of the members is de~ormed radially to generate a sur-face contact between the sealing surfaces. Since the sealing of the pin has a higher taper or angle of in-15 cline with respect to the coaxial axis of the pin andbox, the trailing edge of the pin sealing surface is the first to contact the annular sealing surface of the box on initial make-up.
The conical and crown-type metal-to-metal seal-20 ing geometries in use today for high pressure joints for the oil and gas industry, typically have pin and box members machined to the same nominal angle of engage-ment as measured from the tubular axis. This angle is typically between two degrees t2) and fifteen degrees 25 (15), but may be of any angle. A typical conical seal of any given width would have both pin and box seals machined to a nominal fourteen degrees (14) for their entire widths. A crown-type seal of fourteen degrees (14) is disclosed in U.S. Patent No. 2,992,019 issued .
30 in the name of MacArthur where a crown seal is provide on the pin member and is machined at the same angle as the sealing surface on the box member.
It has been found that for parallel or near parallel mating surfaces such as sealing surfaces of ` 35 conical or crown-type metal-to-metal seals of the same or substantially the same angles, the bearing loads shift .
131696~
from the leading edge of the seal on initial contact to the trailing edge upon final make-up. Depending on the amount of radial interference induced, the leading seal edge can be depleted of all bearing load as the load is 5 transferred further and further bacX toward the trailing seal edge with the increase in metal-to-metal inter-ference. ~t very high levels of interference the trail-ing edge of the seal can receive bearing loads sufficient to cause not only unnecessarily high stress levels of 10 interfexence in the seal area, but even yielding of the material in a seal surface. This yielding or plastic metal surface distortion, sometimes also referred to as galling, can lead to the metal-to-metal seal losing its pressure containment ability. For this reason, the amount 15 of interference between sealing members has heretofore been limited to avoid attainment of the galling thre~h~l~.
This, however, has tended to lower the maximum pressure containment limit of typical metal-to metal seals, par-ticularly on thick wall, high yield strength tubular 20 goods.
The metal-to-metal seal described in U.S. Patent No. 2,893,759 mentioned above provides that the angle of incline of the sealing surface on the pin member be greater than the angle of incline of the sealing surface 25 on the box member. This arrangement necessarily causes the trailing edge of the pin sealing surface to first ; come in contact with the sealing surface on the box mem-ber and upon further make-up, at least one of the mem-bers is deformed radially whereby the bearing load on 30 the final seal is greatly distorted ~at a particular point, typically~the trailing edge of the seal.
It is therefore an object of this invention to provide a metal-to-metal seal in a tubular joint that has a substantiall~ uniform loading distribution 35 across the axial extent of the metal-to-metal contact between the male and female members.
.
, . .
fl// 1 3 1 6 9 6 ~-lr The present invention therefore provides a tubing joint comprising, tubular pin and box members for coaxial mating, the box member having a counterbore for receiving the pin member and having an annular inwardly facing internal shoulder inclining at an angle with respect to the axis of the box member, the pin member having a conical internal shoulder at its free end for coaxial mating with said box member annular shoulder, said pin member having a thick wall and a high yield strength in the vicinity of said internal pin shoulder, said internal pin shoulder inclining inwardly toward the end of the pin member, the angle of incline of said internal pin shoulder with respect to the pin axis being less than the box internal shoulder incline angle, whereby upon coaxial mating of said shoulders the bearing load distribution across said shoulders is approximately uniform, and mating threads on the box and pin members respectively spaced from said shoulder.s outwardly on the box member and outwardly on the pin member, said pin member having its internal shoulder formed on the exterior wall of a length of substantially solid cylindrical tubing, said tubing having a substantially smooth internal bore in the axial vicinity of said internal pin shoulder.
The present invention also provides a tubing joint comprising, tubular pin and box members for coaxial mating, the box member and having a counterbore for receiving the pin member and having an annular inwardly facing external shoulder inclining at an angle with respect to the axis of the box member, the pin member having a conical external shoulder at its fixed end for coaxial mating with said box member annular shoulder, said external pin shoulder inclining inwardly toward the free end of the pin member, the angle of incline of said external box shoulder with respect to the box axis being ~J
.
-4a- 1 31 6q64 -less than the pin external shoulder incline angle and, mating threads on the box and pin members respectively spaced from said shoulders inwardly on the box member and outwardly on the pin member.
Further features and advantages of this invention will be more readily understood from the following description of the preferred embodiments of the invention taken together with the accompanying drawings wherein:
Figure 1 is a longitudinal section of a fully made-up tubular joint embodying the principles of the invention with only part of the joint being shown, and the rest being broken away;
:: :
,.: . . .
.
" 1 31 696~
Figure 2 is a representation of conical sealing surfaces on the box and pin members;
Figure 3 is a representation of a crown-type seal on a pin member for sealing with a conical surface 5 on the box member;
Figure 4 represents a made-up sealing surface of ~:
a box and pin member and shows the stress distribtuion when the seal is fully made-up;
Figure 5 shows the bearing loads on a fully lO made-up sealing surface where the angles of incline are substantially the same for the box and pin members;
Figure 6 shows conical sealing surfaces ac-cording to the invention where the angle of incline of the pin sealing surface is less than that of the box 15 sealing surface;
Figure 7 shows a fully made-up seal between the box and pin members where the angle of incline of the pin member is less than that of the box member and ad-ditionally shows the stress distribution across the width 20 of the sealing surface;
Figure 8 shows a crown-type sealing surface on a pin member as it initially is being made up with a conical surfaced box member; and ` Figure 9 shows a fully made-up sealing surface 25 of crown-type surface on a pin member and conical box member and showing th~ stress distribution across the axial width of the sealing surface.
~ Figure l shows a typical tubing joint lO com-: prising box member 20 and pin member 30 with two step 30 threads 21 and 22. Tubing joint lO has an external seal 40 and an:internal seal 50 for sealing against external ~-and internal pressure differences caused by high pres-sure fluid and gas, either inside or external to the :tubing joint.
35 : Figure 2 illustrates a metal-to-metal seal in :: : ~
:
!
- 6 _ 1316~6~ :
use today in the oil and gas industryO These seals comprise members machined to the same nominal angle of engagement from the tubing axis. Figure 2 represents a conical metal-to-metal seal and may be used to rep-5 resent either an internal seal 50 or an external seal 40 as in Figure 1. For the case of an internal seal, element 70 represents the pin member while element 80 represents the box member. For the case of an external seal, element 80 represents the box memher (element 20 10 in Figure 1) while element 80 represents pin member (element 30 in Figure 1).
The angle ~f engagement as shown in Figure 2 for prior art metal-to-metal seals is usually between two degrees (2) and fifteen degrees (15) but may be of 15 any angle. For instance, a typical conical seal of a nominal fourteen degrees (14) of any given width would have both pïn and box seals machined to a nominal four-teen degrees tl4) for the entire widths.
Similarly, Figure 3 shows a metal-to-metal seal 20 wherein element 71 represents a crown-type seal where surface 72 is machined to be fourteen degrees (14) for engagement with a nominal fourteen degree (14) incline L
of element 81. As the description of Figure 2 indicated in a similar fashion, element 81 represents the box 25 member for an internal seal with element 71 being the pin member and vice versa for the external seal il-lustrated at 40 in Figure 1.
Figure 4 illustrates a conical-type seal, where elements 70 and 80 represent either pin and box 30 elements (depending upon whether the seal under review is an internal seal or an external seal) and where the ~-sealing surfaces 70' and 80' are machined to substantial-ly the~same angle. A stress distribution represent~tion is illustrated as a function of axial contact length be-35 low the contacting surfaces 70l and 80' when the sur-.
faces are fully made-up. Figure 4 illustrates that a higher stress levels in one area of the sealing surface, the trailing edge of the surface, may become extremely high. The leading and trailing edge as used herein are 5 measured with respect to the member having the least thickness of metal, that is with respect to the pin surface for an internal seal, the box surface for an external seal. If the stress level is extreme in one section of the seal, the metal-to-metal seal may become 10 subjec~ to premature galling and the surrounding geo-metry could become subject to increased incidence of stress induced preferential corosion or fatigue failure. Similarly, if the bearing load gets too high, the material could yield allowing the possible passage 15 of previously contained fluid or gas.
Figure 5 illustrates how the extreme high b~ar--ing loads on the seals having substantially equal in-clining surfaces can cause member 70 to rock about the trailing edge of the sealing surface and ultimately lead 20 to the problems discussed above.
Figure 6 shows a sealing surface according to the invention where the sealing surface 75 is machined at an angle A' with respect to its axis somewhat less than tha angle A of sealing surface 85 of element 80. As 25 discussed above if the sealing arrangement of Figure 6 is used as an internal seal, element 70 represents the pin member 30 and element 80 represents the box member 20. As the element 70, representing a pin member of an internal seal is initially made-up with the female 30 member or box member 80, it makes initial contact with box member 80 at cylindrical line 100. It is apparent that on initial mating, the bearing load is substantial-ly on the leadin~ edge of the pin shoulder with the trailing edge of the box shoulder.
a 1 31 696~
It should be apparent that Figure 6 also rep-resents ~he case for an external seal where element 70 represents the box member and element 80 represents the pin member. Where Figure 6 represents an internal 5 seal, element 70 representing the pin member is machined to be a lower taper or incline angle than that of the box member 80. Where Figure 6 represents an external seal, the box sealing surface 70 is machined to a smaller angle than that of the pin member 80.
Figure 7 shows the elements 70 and 80 in a fully made-up condition and indicates with a stress versus length diagram beneath the seal that the stress as a function of axial width is uniform and, in this case, a "U" shape.
Figure 8 represents a box element 81 and a pin element 71 for an internal seal in which the crown sur face 72 of element 71 is adapted for mating with conical surface 82 of element 81. According to the invention, the angle of incline of surface 72 of element 71 is 20 machined to be less than the~angle of incline of surface 82 of element 81 such that the leading edge of element 71 engages element 81 at the cylindrical line 76 about the conical surface. Figure 8 illustrates that the angle ;;
B' or the incline of the element 71 about the axis of -25 element 72 is less than the angle B which represents the angle of incline of sealing surface 82 of element 81.
Figure 9 shows the crown sealing surface 72 of element 71 in the fully made-up position and illustrates the stress distribution across the axial width of the ~
- ; 30 sealing surface. As illustrated, the stress distribution ~is uniform in width and is "U" shaped. As discussed ~with respect to Flgure 6 for the conical sealing sur-faces, the crown sealing surface represented in Figure 8 may be located at other regions of the tubular con-35 nection and used for either an internal seal, an external seal, or both an internal and an external seal. In this 9,, ': - .
' , ' . ' " ' '~
: ~
1 31 6q6~
g example, an internal seal element 81 would represent 3 the box member while element 71 would represent the pin member. Likewise, for an external seal as at 40 in Figure 1, element 81 would represent the pin member while 5 element 71 would represent the box memberO
According to the invention as illustrated in s;
the sealing arrangements of Figures 6 and 8, the exact mismatch of the sealing surfaces will vary depending on the seal angle of the more rigid member, the width of 10 the sealing surface, the thickness of the thinner member relative to its seal diameter, the thickness of the thinner member relative to the thickness of the thicker member at the seal region, desired tolerances, and other factors. For example, it can be shown that seal 15 mismatch for very low angle seals of approximately one-half inch (1/2") in axial width can be as low as one quarter degree (1/4), and high angle seals of equal axial width may require a mismatch of one degree (1) or more for complete balancing of bearing loads upon 20 full make-up~ Finite element analysis may be used as a tool to verify the optimum seal angle mismatch on any given seal and connection geometry.
The sealing surfaces according to the invention may be used either singularly as an internal seal, ~ -25 singularly as an external seal, or may be used together in a tubular connection having both an internal and ex-ternal seal.
From the foregoing, it is apparent that there has been provided a sealing surface for use in joints 30 interconnecting tubular members used in oil and gas ,~
wells. Various modifications and alterations in the described structures will be apparent to those s~illed in the art from the foregoing description which do not depart from the scope of the invention~
b~
Claims (34)
1. A tubing joint comprising, tubular pin and box members for coaxial mating, the box member having a counterbore for receiving the pin member and having an annular inwardly facing internal shoulder inclining at an angle with respect to the axis of the box member, the pin member having a conical internal shoulder at its free end for coaxial mating with said box member annular shoulder, said pin member having a thick wall and a high yield strength in the vicinity of said internal pin shoulder, said internal pin shoulder inclining inwardly toward the end of the pin member, the angle of incline of said internal pin shoulder with respect to the pin axis being less than the box internal shoulder incline angle, whereby upon coaxial mating of said shoulders the bearing load distribution across said shoulders is approximately uniform, and mating threads on the box and pin members respectively spaced from said shoulders outwardly on the box member and outwardly on the pin member, said pin member having its internal shoulder formed on the exterior wall of a length of substantially solid cylindrical tubing, said tubing having a substantially smooth internal bore in the axial vicinity of said internal pin shoulder.
2. The tubing joint of claim 1 wherein on initial mating of said internal box shoulder with said internal pin shoulder, the bearing load substantially on the leading edge of said pin shoulder with the trailing edge of said box shoulder.
3. The tubing joint of claim 1 wherein the angle difference between the box outwardly inclining shoulder and the pin inwardly inclining surface is selected such that the bearing load across the entire axial width of the seal of mating box and pin shoulders is a relatively even distribution at final make-up.
4. The tubing joint of claim 3 wherein said bearing load distribution at final make-up as a function of distance across the axial width of the seal of mating box and pin shoulders is "U" shaped.
5. The tubing joint of claim 1 wherein said internal shoulder of the pin member is one frustro-conical sealing surface of two or more frustro-conical surfaces arranged along the end of said pin member.
6. The tubing joint of claim 1 wherein the pin and box members have engageable threads, and the internal shoulder of the box member is a first conical sealing surface provided axially inwardly of said threads, internal shoulder of the pin member is a complementary second conical sealing surface adapted to engage substantially throughout its axial width with the first sealing surface to seal the joint.
7. The tubing joint of claim 6 whereby on initial mating of said first conical sealing surface provided on the box member with the second conical sealing surface provided on the pin member, the bearing load is substantially on the leading edge of said second conical sealing surface with the trailing edge of said first conical sealing surface.
8. The tubing joint of claim 6 wherein the angle difference between said angles is selected such that the bearing load across the entire axial width of the seal of mating box conical sealing surface is relatively even distribution at final make-up.
9. The tubing joint of claim 8 wherein said bearing load distribution as a function distance across the axial width of mating pin and box sealing surfaces is "U".
10. The tubing joint of claim 6 wherein said second conical sealing surface provided on the pin member is one frustro-conical sealing surface of two or more frustro-conical sealing surfaces arranged along the axis of said male member.
11. A pin member adapted for connection to a box member to form a tubing joint, said box member having a counterbore for receiving the pin member and having an annular inwardly facing internal shoulder inclining at an angle with respect to the axis of the box member, said box member having threads spaced axially outwardly from said internal shoulder, said pin member comprising, a conical internal shoulder at its free end for coaxial mating with said box member annular shoulder, said pin member having a thick wall and high yield strength in the axial vicinity of said internal shoulder, said internal pin shoulder inclining inwardly toward the end of the pin member, the angle of incline of said internal pin shoulder with respect to the pin axis being less than the box internal shoulder incline angle when said pin member is coaxially mated with said box member, said pin member having its internal shoulder formed on the exterior wall of a length of substantially solid cylindrical tubing, said tubing having a substantially smooth internal bore in the axial vicinity of said internal pin shoulder, and pin member threads spaced outwardly from said conical internal shoulder and mating with said box member threads when said pin member is coaxially inserted and rotated in said box member, whereby upon coaxial mating of said shoulders the bearing load distribution across said shoulder is approximately uniform.
12. The pin member of claim 11 wherein on initial mating of said pin member with said box member to create a tubing joint, the bearing load is substantially on the leading edge of said pin shoulder with the trailing edge of said box shoulder.
13. The pin member of claim 11 wherein the angle difference between the box outwardly inclining shoulder and the pin inwardly inclining shoulder is selected such that the bearing load across the entire axial width of the seal when the pin shoulder mates with the box shoulder is a relatively even distribution at final make-up.
14. The pin member of claim 1 wherein said internal shoulder of the pin member is one frustro-conical sealing surface of two or more frustro-conical surfaces arranged along the end of the pin member.
15. A box member adapted for connection to a pin member to form a tubing joint, said pin member having a conical internal shoulder at its free end for insertion in the box member and having an internal pin shoulder inclining inwardly toward the free end pin member at an angle with respect to the axis of the pin member, said pin member having threads spaced outwardly from said internal shoulder, said pin member having a thick wall and a high yield strength in the axial vicinity of said internal shoulder, said pin member having its internal shoulder formed on the exterior wall of a length of substantially, solid cylindrical tubing, said tubing having a substantially smooth internal bore in the axial vicinity of said internal pin shoulder said box member comprising, a counterbore for receiving the pin member and having an annular inwardly facing internal shoulder inclining at an angle with respect to the axis of the box member, the angle of incline of said internal box shoulder with respect to the box axis being greater than the pin internal shoulder incline angle when said pin member is coaxially mated with said box member, and box member threads spaced outwardly from said box internal shoulder, and mating with said pin member threads when said pin member is coaxially inserted and rotated in said box member, whereby upon coaxial mating of said shoulders the bearing load distribution across said shoulders is approximately uniform.
16. The box member of claim 15 wherein on initial mating of said box member with said pin member to create a tubing joint, the bearing load is substantially on the leading edge of said pin shoulder with the trailing edge of said box shoulder.
17. The box member of claim 15 wherein the angle difference between the box outwardly inclining shoulder and the pin inwardly inclining shoulder is selected such that the bearing load across the entire axial width of the seal when the pin shoulder mates with the box shoulder is an relatively even distribution at final make-up.
18. The box member of claim 17 wherein said bearing load distribution at final make-up as a function of distance across the axial width of the seal of mating box and pin shoulders "U" shaped.
19. A tubing joint comprising, tubular pin and box members for coaxial mating, the box member having a counterbore for receiving the pin member and having an annular inwardly facing external shoulder inclining at an angle with respect to the axis of the box member, the pin member having a conical external shoulder at its fixed end for coaxial mating with said box member annular shoulder, said external pin shoulder inclining inwardly toward the free end of the pin member, the angle of incline of said external box shoulder with respect to the box axis being less than the pin external shoulder incline angle and, mating threads on the box and pin members respectively spaced from said shoulders inwardly on the box member and outwardly on the pin member.
20. The tubing joint of claim 19 wherein on initial mating of said external box shoulder with said external pin shoulder, the bearing load is substantially on the leading edge of said box shoulder with the trailing edge of said pin shoulder.
21. The tubing joint of claim 19 wherein the angle difference between the box outwardly inclining shoulder and the pin inwardly inclining surface is selected such that he bearing load across the entire axial width of the seal of mating box and pin shoulder is a relatively even distribution at final make-up.
22. The tubing joint of claim 21 wherein said bearing load distribution at final make-up as a function of distance across the axial width of the seal of mating box and pin.
23. A pin member adapted for connection to a box member to form a tubing joint, said box member having a counterbore for receiving the pin member and having an annular inwardly facing external shoulder incline at an angle with respect to the axis of the box member, said box member having threads spaced inwardly from said external shoulder, said pin member comprising, a conical external shoulder at its fixed end for coaxially mating with said box member annular shoulder, said external pin shoulder inclining inwardly toward the end of the pin member, the angle of incline of said external box shoulder with respect to the box axis being less than the pin external shoulder incline angle when said pin member is coaxially mated with said member, and pin member threads spaced outwardly from conical internal shoulder and adapted for mating with said box threads when said pin member is coaxially inserted and rotated in said box member.
24. The pin member of claim 23 wherein on initial mating of said pin member to create a tubing with said box member joint, the bearing load is substantially on the leading edge of said box shoulder with the trailing edge of said pin shoulder.
25. The pin member of claim 23 wherein the angle difference between the box outwardly inclining shoulder and the pin inwardly inclining shoulder is selected such that the bearing load across the entire axial width of the seal when the pin shoulder is a relatively even distribution at final make-up.
26. A box member adapted for connection to a pin member to form a tubing joint, said box member adapted for coaxial mating with a pin member having a conical external shoulder at its fixed end for insertion in the box member and having an external pin shoulder inclining inwardly toward the free end of the pin member, at an angle with respect to the axis of the pin member, said pin member having threads spaced inwardly from said external shoulder said box member comprising, a counterbore for receiving the pin member and having an annular inwardly facing external shoulder inclining at an angle with respect to the axis of the box member, the angle of incline of said external pin shoulder with respect to the pin axis being greater than the box external shoulder incline angle when said pin member is mated with said box member, box member and threads spaced inwardly from said box external shoulder and mating with said pin member threads when said pin member is coaxially inserted and rotated in said box member.
27. The box member of claim 26 wherein on initial mating of said box member with said pin member to create a tubing joint, the bearing load is substantially on the leading edge of said box shoulder with the trailing edge of said pin shoulder.
28. The box member of claim 26 wherein the angle difference between the box outwardly inclining shoulder and the pin inwardly inclining shoulder is selected such that it is selected such that the bearing load across the entire axial width of the seal when the pin shoulder mates with the box shoulder is a relatively even distribution at final make-up.
29. The box member of claim 26 wherein said bearing load distribution at final make-up as a function of distance across the axial width of the seal of mating box and pin shoulder is "U" shaped.
30. The tubing joint of claim 19 wherein the box member further includes an annular inwardly facing internal shoulder inclining at a second angle with respect to the axis of the box member, and wherein the pin member further include a conical internal shoulder at its free end for coaxial mating with said box member internal shoulder, said internal pin shoulder inclining inwardly toward the end of the pin member, the angle of incline of said internal pin shoulder with respect to the pin axis being less than the box internal second angle, and wherein the mating threads on the box and pin members respectively are spaced between said internal and external shoulders.
31. The tubing joint of claim 30 wherein on initial mating of said external box shoulder with said external pin shoulder, the bearing load is substantially on the leading edge of aid box external shoulder with the trailing edge of said pin external shoulder, and on initial mating of said internal box shoulder with said internal pin shoulder, the bearing load is substantially on the leading edge of said pin internal shoulder with the trailing edge of said box internal shoulder.
32. The tubing joint of claim 30 wherein, the angle difference between the internal box outwardly inclining shoulder and the pin internal inwardly inclining surface is selected such that the bearing load across the entire axial width of the seal of mating box and pin internal shoulder is a relatively even distribution at final make-up, and the angle difference between the external box outwardly inclining shoulder and the pin external inwardly inclining surface is selected such that the bearing load across the entire axial width of the seal of mating box and pin external shoulders is relatively even distribution a final make-up.
33. The pin member of claim 23 wherein said box member further includes an annular inwardly facing internal shoulder inclining at an angle with respect to the axis of the box member, said box member threads are spaced between said external and internal shoulders, said pin member further includes a conical internal shoulder at its free end for coaxial mating with said box member internal shoulder, said internal pin shoulder inclining inwardly toward the free end of the pin member, and the angle of incline of said internal pin shoulder with respect to the pin axis being less than the box internal shoulder incline angle when said pin member is coaxially mated with said box member, said pin member having its internal shoulder formed on the exterior wall of a length of substantially solid cylindrical tubing, said tubing having a substantially smooth internal bore in the axial vicinity of said internal pin shoulder, and wherein said pin member threads are spaced between said pin internal and external shoulders.
34. The box member of claim 26 wherein said pin member further includes a conical internal shoulder at its free end for insertion in the box member and having an internal pin shoulder inclining inwardly toward the free end of the pin member at an angle with respect to the axis of the pin member, said pin member threads are spaced between said external and internal shoulders, said box member further includes an annular inwardly facing internal shoulder inclining at an angle with respect to the axis of the box member, and the angle of incline of said internal box shoulder with respect to the box axis being greater than the pin internal shoulder incline angle when said pin member is coaxially mated with said box member, and said box member threads are spaced between said box internal and external shoulders.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US06/458,732 US5423579A (en) | 1983-01-17 | 1983-01-17 | Tubular coupling with metal to metal seal |
| US458,732 | 1983-01-17 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1316964C true CA1316964C (en) | 1993-04-27 |
Family
ID=23821868
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000445363A Expired - Lifetime CA1316964C (en) | 1983-01-17 | 1984-01-16 | Tubular coupling with improved metal to metal seal |
Country Status (10)
| Country | Link |
|---|---|
| US (1) | US5423579A (en) |
| EP (1) | EP0131622B1 (en) |
| JP (1) | JPS60500458A (en) |
| CA (1) | CA1316964C (en) |
| DE (1) | DE3472817D1 (en) |
| DK (1) | DK438684A (en) |
| IT (1) | IT1178075B (en) |
| MX (1) | MX159680A (en) |
| SG (1) | SG30689G (en) |
| WO (1) | WO1984002948A1 (en) |
Families Citing this family (29)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4817962A (en) * | 1987-12-28 | 1989-04-04 | The Hydril Company | Universal tubular connection having a variable metal-to-metal seal width corresponding to material yield strength |
| GB8802238D0 (en) * | 1988-02-02 | 1988-03-02 | Shell Int Research | Pressure energized sealing joint |
| IT1224745B (en) * | 1988-10-03 | 1990-10-18 | Dalmine Spa | METALLIC HERMETIC SEAL JOINT FOR PIPES |
| US4945434A (en) * | 1988-12-05 | 1990-07-31 | Maxtor Corporation | Magnetic recording head employing an I-bar core structure |
| DE69535474T2 (en) * | 1994-10-19 | 2008-01-03 | Vallourec Mannesmann Oil & Gas France | Threaded connection for pipes |
| US5871473A (en) * | 1996-10-04 | 1999-02-16 | United States Surgical Corporation | Cannula housing connection |
| WO1999018382A1 (en) * | 1997-10-08 | 1999-04-15 | Sumitomo Metal Industries, Ltd. | Screw joint for oil well pipes and method of manufacturing same |
| US6283511B1 (en) | 1998-08-24 | 2001-09-04 | Well Engineering Partners, B.V. | Pipe coupling |
| US6254146B1 (en) * | 1999-04-23 | 2001-07-03 | John Gandy Corporation | Thread form with multifacited flanks |
| IT1318179B1 (en) * | 2000-07-17 | 2003-07-23 | Dalmine Spa | INTEGRAL THREADED JOINT FOR PIPES. |
| US6811189B1 (en) * | 2000-10-04 | 2004-11-02 | Grant Prideco, L.P. | Corrosion seal for threaded connections |
| US6749020B1 (en) * | 2000-11-07 | 2004-06-15 | Benoit Machine Inc. | Well screen two step coupled connector structure |
| US6550821B2 (en) | 2001-03-19 | 2003-04-22 | Grant Prideco, L.P. | Threaded connection |
| JP3876656B2 (en) | 2001-07-13 | 2007-02-07 | 住友金属工業株式会社 | Threaded joints for pipes |
| US6607220B2 (en) | 2001-10-09 | 2003-08-19 | Hydril Company | Radially expandable tubular connection |
| US7513537B2 (en) * | 2003-10-22 | 2009-04-07 | Frank's Casing Crew & Rental Tools, Inc. | Tubular connection with slotted threads |
| JP2005351324A (en) * | 2004-06-09 | 2005-12-22 | Metal One Corp | Screw joint for oil well pipe |
| CA2481609A1 (en) * | 2004-09-28 | 2006-03-28 | Argus Machine Co. Ltd. | Threaded connection for drill pipes |
| US20060071473A1 (en) * | 2004-10-05 | 2006-04-06 | Sivley Robert S Iv | Helical groove for a tubular connection |
| US7497481B2 (en) | 2005-05-13 | 2009-03-03 | Hydril Llc | Treating method and design method for tubular connections |
| US8177262B2 (en) * | 2005-07-28 | 2012-05-15 | Hydril Company Lp | Mid-seal for expandable connections |
| EP2339218A1 (en) * | 2009-12-18 | 2011-06-29 | Uponor Innovation AB | A connection between two pipe parts |
| FR2961576B1 (en) * | 2010-06-17 | 2012-08-03 | Vallourec Mannesmann Oil & Gas | THREADED JOINT AND METHOD OF MAKING |
| DE102011007660A1 (en) * | 2011-04-19 | 2012-10-25 | Hilti Aktiengesellschaft | Hand tool and manufacturing process |
| KR101251535B1 (en) * | 2011-11-30 | 2013-04-05 | 현대자동차주식회사 | Oil pump for vehicle |
| BR112019004059B1 (en) * | 2016-09-30 | 2022-10-04 | Jfe Steel Corporation | THREADED JOINT FOR STEEL PIPE FOR OIL WELLS |
| JP6946749B2 (en) * | 2017-05-30 | 2021-10-06 | 株式会社ジェイ・エム・エス | Female connector |
| BR112022004592A2 (en) * | 2020-01-17 | 2022-07-26 | Nippon Steel Corp | THREADED CONNECTION FOR TUBE |
| CN114198539B (en) * | 2020-09-02 | 2023-11-28 | 盾安环境技术有限公司 | flow valve |
Family Cites Families (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US951704A (en) * | 1906-12-14 | 1910-03-08 | Charles R Schmidt | Pipe-coupling. |
| US2006520A (en) * | 1933-07-17 | 1935-07-02 | Hydril Co | Casing joint |
| US2211179A (en) * | 1938-11-12 | 1940-08-13 | Hydril Company Of California | Casing joint |
| US2239942A (en) * | 1939-05-17 | 1941-04-29 | Hydril Company Of California | Well pipe joint |
| US2258066A (en) * | 1940-03-11 | 1941-10-07 | Youngstown Sheet And Tube Co | Pipe joint |
| GB539139A (en) * | 1940-09-23 | 1941-08-28 | James Cuthill | Improvements in fluid pressure joints for pipes and other conduits, fittings and the like |
| US2450453A (en) * | 1945-07-24 | 1948-10-05 | Hughes Tool Co | Double seal grip tool joint |
| US2505747A (en) * | 1948-03-19 | 1950-04-25 | Nat Supply Co | Tight threaded joint |
| US2574081A (en) * | 1949-04-18 | 1951-11-06 | Walter A Abegg | Pipe joint |
| US2774081A (en) * | 1953-10-08 | 1956-12-18 | Eino J Lukala | Constructions for demountable cribs |
| US2893759A (en) * | 1957-05-06 | 1959-07-07 | Smith Corp A O | Conically tapered screw-type casing joint with metal-to-metal seal |
| US2992019A (en) * | 1958-07-07 | 1961-07-11 | Hydril Co | Casing joint having metal-to-metal sealing means responsive to fluid pressure |
| FR1489013A (en) * | 1965-11-05 | 1967-07-21 | Vallourec | Assembly joint for metal pipes |
| US3606403A (en) * | 1969-07-02 | 1971-09-20 | Fiberglass Resources Corp | Pipe joint |
| DZ508A1 (en) * | 1982-02-18 | 2004-09-13 | Vallourec | New seal for high pressure tight steel tubes and not very sensitive to seizure. |
| US4508375A (en) * | 1982-09-20 | 1985-04-02 | Lone Star Steel Company | Tubular connection |
-
1983
- 1983-01-17 US US06/458,732 patent/US5423579A/en not_active Expired - Lifetime
-
1984
- 1984-01-13 EP EP84900780A patent/EP0131622B1/en not_active Expired
- 1984-01-13 JP JP59500824A patent/JPS60500458A/en active Pending
- 1984-01-13 DE DE8484900780T patent/DE3472817D1/en not_active Expired
- 1984-01-13 WO PCT/US1984/000039 patent/WO1984002948A1/en active IP Right Grant
- 1984-01-16 MX MX200046A patent/MX159680A/en unknown
- 1984-01-16 CA CA000445363A patent/CA1316964C/en not_active Expired - Lifetime
- 1984-01-17 IT IT47547/84A patent/IT1178075B/en active
- 1984-09-14 DK DK438684A patent/DK438684A/en not_active Application Discontinuation
-
1989
- 1989-05-11 SG SG306/89A patent/SG30689G/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| IT8447547A0 (en) | 1984-01-17 |
| MX159680A (en) | 1989-08-02 |
| DK438684D0 (en) | 1984-09-14 |
| SG30689G (en) | 1989-09-29 |
| EP0131622B1 (en) | 1988-07-20 |
| JPS60500458A (en) | 1985-04-04 |
| US5423579A (en) | 1995-06-13 |
| WO1984002948A1 (en) | 1984-08-02 |
| DK438684A (en) | 1984-11-16 |
| EP0131622A1 (en) | 1985-01-23 |
| DE3472817D1 (en) | 1988-08-25 |
| IT1178075B (en) | 1987-09-09 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |