US4548431A | 1985-10-22 | |||
US5154452A | 1992-10-13 | |||
US4946201A | 1990-08-07 |
1. | What is claimed is: A tubular drilling member having a pin connector at one end and a box connector at the other end, each connector being adapted to mate with a connector similar to that at the opposite end of the drilling member but on another such member, to form a tool joint; the pin connector comprising: a pin tong section of relatively large transverse dimension; a pin base section outwardly adjacent the pin tong section and of smaller transverse dimension, whereby an external, annular, generally axially facing primary shoulder is defined between the pin tong and pin base sections; a tapered threaded section outwardly adjacent the pin base section; a pin nose section outwardly adjacent the threaded section and of smaller outer diameter than the small end of the threaded section, the pin nose section having an annular pin end face; the box connector comprising: an internal, generally axially facing, annular secondary shoulder sized to align with such pin end face in such tool joint; a box base section outwardly adjacent the secondary shoulder and sized to receive such pin nose section; a tapered threaded section outwardly adjacent the box base section and adapted to mate with the threaded section of such pin connector; a box counterbore section outwardly adjacent the threaded section of the box connector, of larger inner diameter than the trough of the largest thread of the box connector, and sized to receive such pin base section; the box counterbore section having an annular box end face sized to align with the primary shoulder; wherein (a) the length of the threaded section of the pin, (b) the transverse crosssectional area of the pin nose, and the smaller of (c), the transverse crosssectional area of the box counterbore section, or (d) the transverse crosssectional area of the last engaged thread of the pin are correlated so that torsional strength of such tool joint is approximately equally dependent on each of (a), (b) and the smaller of (c) or (d). |
2. | The apparatus of Claim 1 , wherein: At _> 1 .73(AL + AN) where: At = thread shear area AL = transverse area of smallest last engaged thread AN = transverse area of pin nose section . |
3. | The apparatus of Claim 2, wherein the outer diameter of the box connector is reduced along the box counterbore section. |
4. | The apparatus of Claim 2, wherein the lengths and thicknesses of the box counterbore, pin base, box base and pin nose sections are selected so that, when such tool joint is made up to 60% of its yield strength, the box end face will tighten against the primary shoulder to a force greater than any force being exerted by the pin end face against the secondary shoulder, with the pin end face tightening against the secondary shoulder if additional torque is encounter during drilling. |
5. | The apparatus of Claim 4, wherein the outer diameter of the box connector is reduced along the box counterbore section. |
Background
The present invention pertains to the connectors, i.e. the
pins and boxes, of tubular drilling members such as drill pipe or
drill collars. It is especially applicable to the type of drill pipe
generally described in U.S. Patent No. 4,548,431 to Hall et al,
and represents an improvement thereover.
Such a pipe has a pin connector at one end and a box
connector at the other end, each connector being adapted to
mate with a connector similar to that at the opposite end of the
pipe -- but on another pipe, to form a tool joint. The type of pin
connector in question comprises a pin tong section of relatively
large outer diameter; a pin base section outwardly adjacent the
pin tong section and of smaller outer diameter, whereby a
primary, generally axially facing, annular shoulder is defined
between the pin tong and pin base sections; a tapered threaded
section outwardly adjacent the pin base section; and a pin nose
section outwardly adjacent the threaded section and of smaller
diameter (by a value c,) than the small end of the threaded
section, the pin nose section having an annular pin end face. The
box connector comprises an internal, generally axially facing,
annular secondary shoulder sized to align with the pin end face
of a similar pipe in a tool joint, a box base section of relatively
small diameter outwardly adjacent the secondary shoulder and
sized to receive the pin nose section; a tapered threaded section
outwardly adjacent the box base section and adapted to mate
with the threaded section of the pin connector; a box counterbore
section outwardly adjacent the threaded section of the box
connector, of larger inner diameter than the trough of the largest
thread of the box connector, and sized to receive the pin base
section, the box counterbore section having an annular box end
face sized to align with the primary shoulder on the pin
connector.
The pipe described in the Hall et al patent is designed to
form tool joints which can withstand higher torque loading than
conventional tool joints. The analysis reflected in this prior patent
was largely limited to the stresses and spring-like qualities of the
pin base, the box counterbore section and the pin nose.
Although testing and finite element analysis were conducted as
a means to confirm the accuracy of the stress analysis, and did
not reveal any potential problems, at least one thread failure of
this type of pipe during service indicated that the torsional
strength of the connection can be limited by the length of the
threaded sections. However, the geometry of the joint is such
that the diameter of the pin nose section, which also effects the
torsional strength, is decreased as the thread length is increased,
thus creating a sort of dilemma.
It was discovered by later tests that, when joints were
designed with the thread length adequate for the smallest
anticipated inside diameter, the cross-sectional area of the pin
nose at the largest inner diameter available was too small. Larger
inside diameters produced a pin nose with inadequate strength
compared to the pin base, the box counterbore section and the
threads. In other words, the joint was not "balanced."
Summary of the Invention
The present invention is directed at the problem of
maximizing the torsional strength of a joint, and also ensuring
that the initial failure mode will be buckling of the pin nose and
box counterbore, rather than shearing of the threads. While
buckling of the pin nose and box counterbore is to be avoided, it
is not catastrophic in that it will not ordinarily cause the drill
string to part. However, if there is a thread failure, the drill string
is likely to part, causing very severe problems indeed.
The present invention accomplishes these objectives by
correlating (a) the length of the threaded section of the pin, (b)
the transverse cross- sectional area of the pin nose, and the
smaller of (c) the transverse cross-sectional area of the box
counterbore, or (d) the transverse cross-sectional area of the last
engaged thread of the pin, so that the torsional strength of the
tool joint is approximately equally dependent on factors (a), (b)
and the smaller of factors (c) and (d) above.
More specifically, these conditions can be satisfied when:
A t _> 1 .73(A L + A N )
where: A t = thread shear area
A L = transverse area of smallest last engaged thread A N = transverse area of pin nose section
The connectors may advantageously incorporate and/or
improve on other features of the prior connectors over which they
improve. For example, the lengths and thicknesses of the box
counterbore, pin base, box base, and pin nose sections are
preferably selected so that, when a tool joint is made up to at
least one half, and preferably 60%, of its yield strength, the box
end face will tighten against the primary shoulder at a force
greater than any force being exerted by the pin end face against
the secondary shoulder, with the pin end face tightening against
the secondary shoulder if additional torque is encountered during
drilling. Likewise, the outer diameter of the box connector may
be reduced along the box counterbore section to provide the
necessary deflectability in that area.
Still other features and advantages of the invention will be
made apparent by the following detailed description, the drawing,
and the claims.
Brief Description of the Drawing
Fig. 1 is a longitudinal quarter sectional view of pin and box
connectors according to the present invention in position for
mating to make up a tool joint.
Fig. 2 is an enlarged detailed view of the area encircled in
Fig. 1 .
Detailed Description
Referring to Fig. 1 , there is shown the pin connector 10 of
one piece of drill pipe in position for mating connection to the box
connector 12 of another piece of drill pipe. It should be
understood that the drill pipes are identical. Therefore, the pipe
carrying pin connector 10 has a box connector similar to 12 at its
other end; likewise the pipe carrying the box connector 12 has a
pin connector similar to 10 at its other end. Except for the
improvements described hereafter, the connectors 10 and 1 2 may
be generally of the type disclosed in prior U. S. Patent No.
4,548,431 , which is incorporated herein by reference.
The pin connector 10 has an enlarged diameter tong section
14. (In the case of a drill collar, the tong section outer diameter
is equal to that of the central section between tool joints.)
Axially outwardly adjacent tong section 14 is a cylindrical pin
base section 16. Section 16 is of smaller transverse dimension,
more specifically smaller outer diameter, than section 14,
whereby a primary annular, generally axially facing shoulder 18
is formed between sections 14 and 1 6. ("Generally axially
facing" herein will mean that the direction in which the surface
faces has a significant axial vector component. In the
embodiment illustrated, shoulder 18 is strictly axially facing, i.e.
no other vector components.) The outer edge of shoulder 18
may be beveled, as shown, and at the inner extremity of shoulder
18, there may be provided a relief groove 20, as explained in
prior U.S. Patent No. 4,548,431 . Axially outwardly of pin base
section 1 6 is the tapered threaded section 22 of the pin
connector. The length of section 22, which will be designated
L^, is shown in Fig. 1 . Axially outwardly of threaded section 22
is a pin nose section 24 which is cylindrical, and has a smaller
outer diameter
than the small end of the threaded section 22 by a value c, (see
c,/2 in Fig. 2). The outer end of nose section 24 defines an
axially facing annular pin end face 26, the corners of which may
be beveled as shown.
The box tong section 31 has a reduced inner diameter 32
equal to the inner diameter of the pin. Box connector 1 2, at the
outer end of section 32, has an internal, annular, axially facing
secondary shoulder 28 sized to align with the pin end face 26
and to abut the pin end face 26 when the tool joint is sufficiently
torqued up. Outwardly adjacent to the shoulder 28 is a
cylindrical box base section 30 of larger inner diameter than the
main body 32, whereby shoulder 28 is formed. The inner edge
of shoulder 28 may be beveled, as shown. Box base section 30
is sized to receive the pin nose section 24.
Axially outwardly adjacent the box base section 30, is the
tapered threaded section 36 of the box connector, which is
adapted to mate with threaded section 22 of the pin connector.
Axially outwardly of the threaded section 36, is a box
counterbore section 38 of larger inner diameter than the trough
of the largest thread of the box connector, and sized to receive
the pin base section 16. The end of the box counterbore section
38 forms an annular axially facing box end face 40 sized to align
with the primary shoulder 18 and to abut shoulder 18 when the
joint is made up.
When the joint is made up, the axial force at abutting
surfaces 18 and 40 will be greater than any such force at
opposed surfaces 26 and 28 (which may or may not abut prior to
the application of additional torque during use). More specifically,
the joint is usually made up to at least about one half of its yield
strength, and preferably to about 60%, and in that condition, the
force at faces 18 and 40 will be greater than the force (if any) at
faces 26 and 28. If additional torque is encountered during
drilling, faces 26 and 28 may further tighten against each other,
but preferably not to a force exceeding that at faces 18 and 40.
As explained more fully in U.S. Patent No. 4,548,431 , these
ends are accomplished by proper selection of the lengths and
thicknesses of the box counterbore 38, pin base 1 6, box base
30, and pin nose 24 sections. It is noted, in particular, that for
purposes of adjusting these relative lengths and thicknesses, the
thickness of the box counterbore section 38 may be reduced by
reducing its outer diameter as indicated at 42. This may allow
the necessary compression of the box counterbore section, as the
enclosed pin base section 16 stretches, in tightening end face 40
against the primary shoulder 18. The aforementioned correlation
of lengths and thicknesses of the various sections can be done,
for example, as per the teachings of prior U.S. Patent No.
4,548,431 .
Indeed, the apparatus, as thus far described, is largely in
accord with prior U.S. Patent No. 4,548,431 , and may also
incorporate other details described therein, such as bench mark
shoulders.
While the features thus far described have been generally
successful in allowing tool joints to handle higher torques, and
achieve other effects described in prior U.S. Patent No.
4,548,431 , at least one thread failure was experienced during
service of such pipe, which indicated that the torsional strength
of the connection could be limited by the length of the threads.
However, the geometry of the connection is such that the
diameter of the pin nose section, which also effects torsional
strength, is decreased as the thread length is increased. It was
found, by further testing, that when connections were designed
with the thread length adequate for the smallest anticipated inside
diameter, the cross-sectional area of the pin nose section at the
largest diameter available was too small. Larger inside diameters
produced a pin nose with inadequate strength compared to the
pin base section, the box counterbore section, and the threads.
In other words the connection was not balanced.
The improvements of the present invention optimize the
thread length and nose diameter for any given inside diameter,
thus maximizing the torsional strength of the connection. These
improvements also ensure that the initial failure mode will be
buckling of the pin nose section and box counterbore section,
rather than shearing of the threads. This is important since
buckling of the pin nose section and box counterbore section are
generally not catastrophic; the drill string will not part because of
such buckling. However, a thread failure is likely to cause the
drill string to part, resulting in extreme difficulties and expense.
Thus, in accord with the present invention (a) the length of
-li¬ the threaded section of the pin, (b) the transverse cross-sectional
area of the pin nose, and the smaller of (c) the transverse cross-
sectional area of the box counterbore section, or (d) the
transverse cross-sectional area of the last engaged thread of the
pin ("smallest last engaged thread" hereafter) are correlated so
that the torsional strength of the tool joint is approximately
equally dependent on each of factors (a), (b) and the smaller of
(c) or (d).
One method of achieving this is to design the connectors so
that:
(I): A t _> 1 .73(A L + A H )
where: A t = thread shear area
A L = transverse area of smallest last engaged thread A N = transverse area of pin nose section
The concept of A t or thread shear area is best understood
by reference to the enlarged thread profile shown in Fig. 2. The
pitch of the thread profile shown is the length P measured from
a point on one thread to the analogous point on the next adjacent
thread. The pitch line l p is a line parallel to the thread crest
through the part of the thread where its thickness is equal to half
of the pitch, i.e. P/2. This pitch line is approximately where the
thread would shear if shearing were to occur. A t , the thread
shear area is the thickness of the thread at the pitch line l p
multiplied by the total length L t of the thread at the pitch line l p ,
i.e. as if the helical thread were straightened and measured as a
straight linear distance.
One way of determining parameters which satisfy
relationship (I), is to begin by postulating relationship (I) as an
equation:
(II) A t = 1 .73 (A L + A N ),
then solving that equation, which may be done by using the
following equations:
(III) A t = L^ TΓ R.
where R t = mean thread radius
where c = pitch line diameter at a chosen gauge point between the last engaged thread and the shoulder 18
q = the distance between the gauge point and the last engaged thread
H = untruncated thread height
S RS = radial dimension of root truncation
T = taper (in inches/ft.)
d = inside diameter (32 in Fig. 1 )
where (VI) D n = nose diameter
c-2( H
(Note: c, is derived from c,/2 [Fig. 3] for the full diameter of the member)
After solving all of the above, about % in. is added to L^,
satisfying the " > " aspect of relationship (I) and ensuring that
failure will not be by thread shearing.
It will be understood that relationship (I) is set up in terms
of areas. Each of these areas, of course, is functionally related
to other variables, such as corresponding diameters. Thus, other
equivalent relationships can be extrapolated, expressed in terms
of different variables. However, a connector design which
complies with any such equivalent relationship should also
comply with the relationship (I).
An alternate technique for designing a tool joint with the
proper correlation between parameters so that the torsional
strength of the tool joint is approximately equally dependent on
each of those parameters, is by an iterative process.
More specifically, one would iterate by following these
steps:
1 . Start with a small inner diameter for the size pipe in
question. (This will produce a relatively large value for A N ).
2. Choose a first outer diameter for the pin nose section,
and calculate the needed thread length L^ based on that diameter
using the following relationship:
(VII) L^ π R t - 1 .73(A L + A N ) = 0
3. Using the thread length L^ obtained in step 2,
recalculate (or determine graphically) a new outer diameter for the
pin nose section using relationship (VI).
4. Using the new nose diameter obtained in step 3,
recalculate the necessary thread length by repeating step 2.
5. Continue to alternate these steps until the nose
diameter and thread length reach equilibrium, or near equilibrium,
i.e. when the solution to equation (VII) is O + applicable tolerance
range, as understood by those in the art.
Various modifications of the above embodiments are within
the skill of the art and the scope of the invention, which is limited
only by the following claims.
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