GB2133159A - Preventing buckling in a drill string - Google Patents

Abstract

A method of preventing buckling of a drill string during drilling of a well in the earth comprises the steps of: (a) measuring the forces on, and the azimuth and inclination of, a segment of the drill string; (b) resolving said forces into the axial and normal compounds applied to the next shallower segment, said axial and normal components being related to measured azimuth and inclination of said segments; and (c) determining the buoyed weight, sliding friction, and external forces applied to said segment of said drill string. Steps (a), (b) and (c) are then repeated for successively shallower segments of said drill string and the resultant axial force on each segment of said drill string is compared with a buckling threshold to indicate when said resultant axial force on any segment exceeds said threshold.

Description

SPECIFICATION A method of preventing buckling in a drill string This invention relates to a method of preventing buckling in a drill string during drilling of a well in the earth.

The problems encountered in drilling through the earth to very deep depths have been well documented and successfully solved. These problems are exacerbated in so-called "extended reach drilling" where the path of the drill bit deliberately deviates substantially from the vertical direction. The insertion of tubulars, drill strings, casings, and tubing into very high angle boreholes is particularly difficult.

Recently, sophisticated technology of electronic measuring and data transmission has been applied to this problem. Many state of the art systems accurately track and control the path of the drill string through the subsurface formations. For example, U.S. Patents 3,622,971 -Arps and 4,021,774 Asmundson, describe apparatusfortracking the path of a drill string through the earth from measurements of azimuth and inclination. The Arps patent includes a computer at the surface of the earth for determining the path from the down hole measurements.

U.S. Patent 3,968,473 shows apparatus for measuring the weight on the drill bit and the torque applied to the drill string. U.S. Patent 3,759,489 describes apparatus for automatically controlling the weight on the bit.

One problem which has not been adequately addressed is the buckling of the segments of a drill string. This causes deflections which in turn cause forces against the hole wall which increases the frictional drag. Also, buckling stresses cause pipe fatigue. Some sections of a borehole may have inclinations 800 to 900 (or greater) from the vertical in which the pipe within that section will not slide through the hole with just the force from its own weight. In this situation, sections of the pipe have to be pushed in order to move.

As a pipe is pushed through a borehole, it will flex and buckle. At each contact with the wall of the borehole, an additional force will be applied against the wall causing additional drag. This creates the cumulative situation of added drag causing needed additional axial force which causes more buckling, more force against the wall and more drag, so as to result in a snowballing effect. A point will be reached where, for a given set of conditions, the force to push the pipe is not available or the pipe can fail. Many alternatives exist to change the given conditions, such as: changing the tubular strings; changing the borehole configuration, i.e., casing, or hole sizes; changing the coefficients of friction; and devising means to create a pushing force.

The criteria for buckling in a drill string are known and are described in: Lubinski, Arthur, and Woods, H.B., "Factors Affecting the Angle of Inclination and Dog-Legging in Rotary Bore Holes," API Drilling and Production Practice, 1953, pp. 222-250; and Woods, H.B., and Lubinski, Arthur, "Practical Charts for Solving Problems on Hole Deviation," API Drilling and Production Practice, 1954, pp.

56-71. The application of these criteria to indicate buckling in actual drilling situations, and in the simulation of such drilling, is an object of the present invention.

It is an object of the present invention to determine whether or not buckling of the drill string will occur under certain drilling conditions so that these conditions can be modified or avoided.

In accordance with the present invention, the axial components of the forces on each segment of < drill string are determined. The resultant axial force on each segment is compared with a buckling threshold. When the resultant axial forces exceed this threshold, a buckling tendency is indicated.

In carrying out the invention, the depth, azimuth, and inclination of each segment of a drill string are measured. The buoyed weight, sliding friction, and external forces applied to the bottom segment of the drill string are determined. For each succeedingly higher segment of the drill string, the axial forces from the next deeper segment are resolved into components related to the azimuth and inclination changes between segments. In this manner, the axial force on each segment of the drill string is determined.

The invention will now be more particularly described with reference to the accompanying drawings, in which: Figure 1 depicts an extended reach drilling operation for which the present invention provides an indication of buckling; Figure 2 is a plan view depicting azimuth; Figure 3 depicts a series of segments of the drill string shown in Figure 1 with the interrelated forces; Figure 4 shows the vector resolution between two segments; Figure 5 is similar to Figure 4 and shows the vector resolution for any two adjacent segments; Figures 6-8 show the resolution of forces between two adjacent segments in a manner which accounts for both inclination and azimuth changes between segments; and Figures 9 and 10 show the buckling criteria for different string and hole makeups.

Referring to the drawings, in Figure 1 a conventional drilling rig 10 is disposed over a borehole 11 A drill string 12 includes the usual drill pipe, stabilizers, collars, and bit. Drilling mud is pumped from a supply sump into the drill string and is returned in a conventional manner. Changes in the drill mud pressure may be used to convey downhole parameters to the surface by using logging while drilling apparatus as described in some of the aforementioned patents. For example, the trajectory of the drill string, including inclination 8 and azimuth A may be transmitted uphole. Also, the weight on bit (WOB) may be derived from downhole measurements, although more conventionally it is determined by measuring the forces on the drill string at the surface and deriving WOB from these measurements.

In accordance with the present invention, determination of a tendency for buckling to occur is made segment by segment in the drill string. As used herein, the term "segment" means a short length of the drill string including bit, collars and drill pipe. Segments of equal characteristics are included in a section. For example, the drill string may be divided into the following sections: Section 1: Bit, 1 segment.

Section 2: Eight drill collars, 8 segments.

Section 3: Drill pipe, 1 segment per joint.

The inclination of each segment is denoted Oj where i is an index specifying successive segments starting with the segment at the bottom. Similarly, as shown in Figure 2, the azimuth of each segment is designated by the azimuth change Ai between segments.

As shown in Figure 1, the measurements of inclination and azimuth for each segment and the measurement of weight on bit are applied to a digital computer 13 which also receives as inputs the buoyed weight W for each segment and the coefficient of friction F, between each segment and the surrounding mud and borehole. These inputs are used to determine the axial force AFi on each segment of the drill string. The digital computer also receives as inputs parameters regarding the strength of each segment of the drill string so that a buckling criteria M/r(sin) is determined for each segment. The actual forces are compared to the buckling criteria for each segment by a comparator 14. If the axial forces exceed the threshold an indication of buckling is provided by an indicator 1 5.

While the borehole can be defined by an actual directional survey as indicated in Figure 1, in the practice of the invention the borehole can also be defined by a simulated survey. As will be apparent from the following description, the present invention can be practiced on line as depicted in Figure 1 or it can be practiced in a simulation of a well drilling operation.

Figure 3 depicts the forces on successive segments of the drill string. For convenience, the segments are shown spaced one from the other so that the force vectors between them can be shown.

These successive segments are denoted by the index 1, 2, 3... i. In the actual implementation under consideration, 2,000 segments are used. Each segment has a buoyed weight W1, W2, W3, W, which is determined from the weight of the drill pipe, collars, or the like, and from the density of the drilling mud being used. Other forces which are applied to each segment include R1, R2,R3... R which is the reaction of the borehole wall to the force applied normal to the wall; F1, F2, F3... F,, which is the frictional drag in both directions of movement;. and PL1, PL2, Pal,... PL, whikch is the point load external force applied to each segment. For example, on the first segment, the external force applied would be the weight on bit.

These forces are resolved into components which act along the axis of the segment and normal to the axis of the segment.

Figure 3 shows the balance of forces over segment 1 and the force vectors applied to segment 2.

These forces are defined as follows: Axial Load Lower ALL1 = 0, because segment 1 is the terminal free body on the string.

Point Load PL1 can be bit weight and/or a hydraulic force across the end of the pipe.

Weight Axial WA1 is the axial component of the weight, Wi; WA1 =W1 cos01 The force vectors and components are resolved so that the Axial Load Upper, ALU 1, is parallel to the axis of segment 1, and ALL2 is parallel to the axis of segment 2. Figure 4 shows an analysis of the resolution of force vectors between the two segments when only a change of inclination is taken into account. Final resolution which accounts for azimuth change is given below. Figure 4A shows the resolution of force vectors between segments 1 and 2. The force vector ALU 1 is known from the resolution of forces on segment 1. The vectored forces applied to segment 2 are as shown. HE is parallel to segment 1. The magnitude of HE is ALU 1. BE is parallel to the axis of segment 2. DH is a straight line.

DE=HE BD l BE a (01-02) DE and a are known.

BE and BD are determined as follows: BE=DE cos =DE cos(#1-#2) DB = DE sin = DE sin (#1-#2) Knowing 01,02, ALU 1, and assuming the force vectors of Figure 4A gives: ALL2 and ALLN2.

Returning to Figure 4, assume that ALLN2 is the normal component reacting to the non-alignment of the two segments.

Axial Load Lower Normal: ALLN2 is the component normal to the axis of segment 2 reacting to the axial load ALU1, ALLN2 =ALU1 sin (#1-#2) Axial Load Lower: ALL2 = ALU1 cos (01-02) Reaction of the Wall Let all the normal force components from ALL2 be taken up by segment 2 with the component ALLN2. The reaction of the wall to segment 1, R1, is the sum of all forces normal to the axis of segment 1.

Friction Force Axial F1 is the friction force along the axis and equals the friction coefficient f1 times the sum of the forces normal to the axis.

F1 =flR1 Summing Forces Normal to the Axis (Figure 4) R1-WNl+ALLN1=0 But,ALLN1=0 R1=WN1=W1 sin #1 Summing Forces Along the Axis (Figure 4) PL1+ALL1+F1-WA1-ALU1=0 But,ALL1=0 PL1 is known W1 is known and WA1=W1 cos #1 F1 is known=f1R1=f1W1 sin #1 Solve for ALU 1, the unknown, AIU=PL+f1W1 sin #1 - Wi cos #1 + ALL1 For Reaction To the Second Free Body (Figure 4J The axial load to the end of segment 2 is: ALL2=ALU1 cos (#1-#2) The normal component, due to the non-alignment of the two vectors ALL2 and ALU1 is: ALLN2 = ALU 1 sin (#1-#2) For lithe Free Body (See Figure 5) Figure 5 depicts two segments (i) and (i+ 1).Follow the procedure previously used to analyze segments 1 and 2.

PLi will be known ALL comes from analysis of (i-i) body ALLNi comes from analysis of (i-i) body Wi will be known #i will be known #i + 1 will be known WAi = Wi cos #i WNi=Wi sin #i Fi = fi Ri Summing Forces 1 to the Axis of Segment (i) Ri+ALLNi-WNi=0 Ri =Wi sin #i-ALLNi Summing Forces Parallel to the Axis of Segment (i) PLi +ALU + Fi-WAi-ALUi=0 The unknown is ALUi, ALUi=PLi +ALLi + Fi-WAi = PLi + ALU + fi (Wi sin 0 - ALLNi) - Wi cos Oi For Reaction to the (i+1) Segment ALLi + 1 =ALUi cos (Oi-Oi+1) ALLNi + 1 = ALUi sin (#i-#1) The inclusion of azimuth changes in the borehole profile necessitates a further resolution of the forces acting on each drill string segment. This resolution is depicted in Figures 6, 7 and 8.

As before, each segment is considered to be a free body in equilibrium. The forces on the body are axial, normal and torsional. The axial forces are: 1 The axial component of the segment buoyed weight.

2. The sliding friction force.

3. An externally applied force, if any, assigned to represent weight-on-bit, for example.

4. The axial component of the force on the body from the next deeper segment.

The normal forces are: 1. The normal component of the segment buoyed weight, acting in the vertical plane through the segment.

2. The normal component of the axial force from the next deeper segment, acting in the vertical plane of the segments.

3. The normal component of the axial force from the next deeper segment, acting perpendicularly to the vertical plane of the segment.

The torsional forces are: 1. The cumulation of applied torque at the bottom of the drill string minus torque -loss due to friction for all of the string deeper than the segment.

2. The torque loss due to friction for the segment. The resultant of the axial forces act on the next shallower segment. The resultant of the normal forces determine the torsional and axial friction forces.

Of the above described forces, only those three that are components of the resultant axial force from the next deeper segment are related to azimuth and inclination changes between segments.

Consider Figure 6.

The resultant axial force from the next deeper segment lies in the vertical plane X-Z, has a length AC, and has an inclination ()j. Let A be the azimuth change between segments. The vertical plane A-D-E contains the current segment. The force AC can be resolved into two components, AD in the plane of the current segment, and CD perpendicular to the current vertical plane. In the current plane, AD has an inclination of 0*,.

BC=DE=ACcos0, (1) AB = AC sin Oi (2) BE=CD=AB sin # (3) AE=AB cos # (4)

0*, = cos-1 (DE/AD) (6) In the vertical plane of the current segment, ADE, the deeper segment has an inclination of #i+1 The component AD from the deeper segment must be resolved into two components in the vertical plane ADE, an axial component along the inclination #i+1, and a normal component perpendicular to the segment i + 1. Consider Figure 7 in the vertical plane of the current segment.

Let p=#i+1-#1* (7) AF = AD cos p (8) FD = AD sin p (9) Thus, the axial resultant force from body i, AC, is resolved into the three components CD perpendicular to the plane ADE, AF in the plane ADE along the axis of body i + 1, and DF in the plane ADE normal to theaxisofthebodyi + 1.

In the above analysis, A is the smaller of the two angles at the intersection ofthe two vertical planes. Let S be the azimuth change between segments i and i + 1. If a is less than900, then A = #.

However, if the azimuth change is greater than 900, as will possibly occur in the more vertical portion of the wellbore, then the inclination angles i+1 and O will be measured in opposite directions. Consider Figure 8.

In this case, p = - Oi+i - 0*. Further, as will be shown later, the normal component of the buoyed weight of segment i + 1 must have an upward direction in order to be consistent with the sign convention chosen.

The sign convention is that axial forces are positive if they act toward the deep end of the borehole and are negative if they act toward the top of the hole. As a result of this invention, axial friction forces are positive if the drill string is going into the hole.

In this manner, the resultant axial forces AL, are determined. This axial force is compared to the buckling criteria as previously indicated. Criteria for helical buckling are given by the Lubinski and Woods articles cited above. In their Figure 2, dashed portions of Curves 1,2, and 3 indicate conditions where helical buckling will occur. Figure 2 was developed assuming the hole angle, a, to be "small". In their later article, Lubinski and Woods extended the theory to include the effect of a, even if the angles were "large". They demonstrated that Figure 2 could be used as shown without modification, provided the scales are changed.The abscissa should be changed from am/r (symbols to be explained later) to m/r (sin a), and the ordinate from &num;/ to [sin a-tan (a0)]/sin a. Therefore, the remainder of this discussion of buckling criteria will be based on the Lubinski and Woods Figure 2 but with scale change as indicated.

In Figure 2, Curve 3 is for a "dimensionless weight" of 2 units, and helical buckling occurs when m/r (sin a) equals 0.4. Likewise, Curve 2 is for a-"dimensionless weight" of 4 units with m/r (sin a) for buckling equal 2, and Curve 3 is for a "dimensionless weight of 8 units with m/r (sin a) equal 10 for buckling.

Table 1, below, lists these values and contains extrapolated values to higher '.'dimensionless weights".

TABLE 1 Weight in Dimensionless Units m/r (sin &alpha;) 2 - .4 4 2 8 10 16 50 32 250 64 1250 We now have all the information necessary to develop simple, easily programmed criteria for helical buckling. Lubinski and Woods use a term which they call a "dirfiensionless unit". The dimensionless unit has a length and a weight.The length in feet of one dimensionless unit is:

and the weight in pounds of one dimensionless unit is

where: E = Young's modulus = 30 x 106psi = 4.32 x 109 lbs/ft2 =2.1 x 108 kPa

for steel = 10.6 x 106 psi =1.53 x 109 ibs/ft | =7.3 x 107kPa

for aluminum p = weight of pipe per unit length in mud, Ibs/in or Ibs/ft = = moment of inertia, ft4 or in4 = ,d64 (Do4-Di4) Do = pipe outside diameter Di = pipe inside diameter In addition, a is the angle of the hole with respect to vertical and r is the radical clearance between the pipe outside diameter and hole wall.

DH-DO r= , feet 2 where DH = hole diameter We can evaluate buckling in terms of the axial compressive force in the pipe thus: axial force weight in dimensionless units = weight of one dimensionless unit AF mp We now have all of the terms necessary to evaluate M (sin a) for any pipe size, hole diameter and hole angle.

Figure 9 shows Table 1 plotted on iog-log paper as the weight in dimensionless units AF (equal to-) vs.

mp M - (sin &alpha;).

r The equation of the curve is:

Therefore, helical buckling will occur when:

EXAMPLE 6 in (15 cm) O.D. x 2 1/4 in (5.7 cm) I.D. collars in 8 3/4 in (21 cm) hole p = 82.6 &num;Ift (123 kg/m) in air= 70.2 &num;Ift (5.85 &num;/in or 104 kg/m) in 10 ppg mud II I=64 (64-2.254)=62.3 in4 (2593 cm4) E = 30 x 106 psi (2.1 x i08kPa)

mp = 57 x 70.2 = 4000 Ibs (1814 kg) 8.75-6 r= - =0.115 ft (3.5 cm) 2(12) Ifa 600 AF = 2.93 (4000) (57/.1 15) (sin 60)0.436 = 1 64,800 Ibs (74753 kg) The complete curve of AF vs. hole angle for 6 in (1 5 cm) x 2 1/4 in (5.7 cm) collars in and 8 3/4 in (21 cm) hole is shown in Figure 10.Also shown in Figure 10 is AF vs. hole angle for 8 in (20 cm) x 3 in (7.6 cm) collars in a 12 1/4 in (31 cm) hole.

The symbols used in the forced equations in one computer for practicing the invention are defined below (for segment i+1) W =buoyed weight of segment WA = axial weight component WN = normal weight component (in vertical plane) PL = assigned point load on the segment, if any FA = axial sliding friction force ALU(i) = resultant axial force for the next deeper segment ALL = axial component of ALU(i) onto i + 1 ALLN =vertical plane normal component for i +1 of ALU(i) ALLH = horizontal normal component of ALU(i) RN = resultant normal force on i +1 CF = coefficient of sliding friction SF = plus or minus 1 to determine the sign of the friction force according to the sign convention The angles used are Oi + 1 = average inclination of segment i + 1 O*(i) = inclination of projection of ALU(i) onto the vertical plane of i + 1 p = the change in inclination between segments the vertical plane of i + 1 ,B(i+1) = average azimuth of i + 1 S = the change in azimuth between segments # = = S if A less than or equal to 900, or 180 -# for a greater than 900 The force equations for segment i + 1 are given below: WA =W cos [#(i+1)] (10) WN =W sin [#(i+1)] for ##90 (11) = W sin [-O(i+1)] for S 2 90 (12) RN = SORT ((ALLN+WN)2 + ALLH2) (13) FA =SFxCFxRN (14) ALU(i+1) =FA+ALL+PL+WA (15) where ALL, ALLN, and ALLH are calculated as projections of the ALU(i) from the next deeper segment.

That is, equations 1 through 9 above apply where, AC = ALU(i) (16) ALL = AF (17) ALLN = FD (18) ALLH. CD (19) Note that the equations for RN, the resultant normal force, involves the square of ALLH and of ALLN + WN. This means that the sign of ALLH is unimportant and only the relative signs of WN and ALLN are important.

The equations for torsional friction loss is: DTQ = CFT x RN x DIA124 (20) where DTQ = incremental torsional friction loss in segment i + 1 CFT = torsional coefficient of friction RN = resultant normal force DIA = outside diameter of segment i + 1 Several possible relationships amorig azimuth changes, inclination changes, and the direction of the axial force ALU(i) from the deeper segment are of interest.

1. If there is no azimuth change, A = O, so ALLH = CD = AB sin A =0 AD = AC = ALU(i) 0* =0 p =#i+1-#i ALL = AF = ALU(i) cos p ALLN = FD = ALU(i) sin p RN = |ALLN+WN| 2. For an azimuth change less than 900, (a) All has the same sign as ALU(i) as long as p is less than 900. For p greater than 900, an impractical case, the profile bend is an acute angle and ALL acts in a direction opposite to ALU(i) (b) ALLN has the same sign as ALU(i) for positive p and the opposite sign for negative p. That is, if the profile is building angle, p is negative, and if ALU(i) is negative (acting toward the surface) then ALLN acts in the same direction as WN. If the profile is dropping angle, p is positive, and if ALU(i) is negative, then ALLN is opposite in direction to WN.

3. For an azimuth change greater than 900, (an impractical case unless inclinations are near vertical), the angle p is defined to be-#i+1-#1*. Because of this definition, (a) ALLN is always opposite in sign to ALU(i) so if ALU(i) is negative (toward the surface) the sign of ALLN will be positive. The geometry shows that for H,+, and 0 t in opposite directions, if ALU(i) is negative, ALLN should be opposite in sign to WN. Therefore, to be consistent, the sign of WN is made negative if the azimuth change is greater than 900.

(b) All has-the same sign as ALU(i) as long as:the absolute value of p is less than 900. If the absolute value of p is greater than 900, ALL will act in an opposite direction to that of ALU(i).

4. For an azimuth and inclination change, ALL' ALU(i) ALLN Ze ALLH =0 As a result of the way the above force equations are defined, there are profile restrictions on either the change in azimuth or the change in inclination between segments as fa-r as the program calculations are concerned. Of course, practically, azimuth and inclination changes are limited to the ability to change,hole direction while drilling so the above equations are more general than necessary.

The invention can be practiced using several different types of commercially available general purpose digital computers.-One actual system which was used in practicing the invention was the Control Data Corp. Cyber 170-750 computer.

The programming required for the practice of the invention will be apparent from the foregoing and from the users' manuals for the particular computer which is used.

Claims (6)

1. A method of preventing buckling of a drill string during drilling of a well in the earth comprising: measuring the forces on, and the azimuth and inclination of, a segment of the drill string; resolving said forces into the axial and normal components applied to the next shallower segment, said axial and normal components being related to measured azimuth and inclination of said segments; determining the buoyed weight, sliding friction, and external forces applied to said segment of said drill string; repeating the aforesaid steps for successively shallower segments of said drill string; comparing the resultant axial force on each segment of said drill string with a buckling threshold; and indicating when said resultant axial force on any segment exceeds said threshold.

2. A method as claimed in claim 1, wherein the step of resolving includes: resolving the buoyed weight, friction and external forces into the axial component along said segment based on the azimuth and inclination of said segment; and resolving said axial component into the axial force applied to the next shallower segment based on the azimuth and inclination of the last named segment.

3. A method as claimed in claim 1 or claim 2, wherein the components of said forces normal to each segment are multiplied by the coefficient of friction to determine the sliding friction for each segment.

4. A method as claimed in claim 1 , wherein the torsional forces reacting each segment are determined and the cumulative torsional forces are determined on all the segments.

5. A method as claimed in any preceding claim, wherein the lowest segment includes a drill bit and wherein the external force applied to said lowest segment is the weight on bit.

6. A method as claimed in claim 1, wherein simulated values are used to predict changes in forces on the drill string corresponding to the simulated values.