Lyons W.C. (ed.). Standard handbook of petroleum and natural gas engineering.2001- Volume 1

Drill String: Composition and Design

745

P

=

(418700)'

-

3

[

(

8.542

Due to the safety factor of

2.0

the tensile load capacity of the drill pipe is

398432/2

=

199,216

lb.

Example

Calculate the maximum value of a rotary torque that may be applied to the drill

pipe as specified in Example

5 if

the actual working tension load P

=

300,000

lb.

(For instance, pulling and trying to rotate

a

differentially stuck drill string.)

Solution

From Equation

4-58,

the magnitude of rotary torque is

so

=

353,571

in-lb

or

29,464

ft-lb

(418,700'

-

300,000)2

4.4074

3

Caution:

No

safety factor is included in this example calculation. Additional

checkup must be done

if

the obtained value of the torque is not greater than

the recommended makeup torque for tool joints.

During normal rotary drilling processes, due to frictional pressure losses, the

pressure inside the drill string

is

greater than that of the outside drill string.

The greatest difference between these pressures is at the surface.

If the drill string is thought to be a thin wall cylinder with closed ends, then

the drill pipe pressure produces the axial stress and tangential stress given by

the following formulas:

(For stress calculations, the pressure loss in the annulus may be ignored.)

'dpDdp

0,

=

4t

2t

(4-59)

(4-60)

where

oa

=

axial stress in psi

ot

=

tangential stress in psi

PdP

=

internal drill pipe pressure in psi

t

=

wall thickness of drill pipe in psi

Ddp

=

outside diameter of drill pipe in in.

746

Drilling and Well Completions

Substituting Equations 459, 4-60, 456, and 4-55 into Equation 4-54 and solving

for the tensile load capacity of drill pipe yields

(4-61)

Example

Find the tensile load capacity of 5-in., nominal weight 19.5-lb/ft, steel grade

E, premium class drill pipe exposed to internal drill pipe pressure P,,

=

3,000 psi

and rotary torque T

=

15,000

ft-lb.

Solution

From Table 4-79 Nominal D,

=

5 in., nominal ddp

=

4.276 in., nominal wall

thickness t

=

0.362. Reduced wall thickness for premium class drill pipe

=

(0.8)(0.362)

=

0.2896 in. Reduced D, for premium class

=

4.276

+

(2)(0.2896)

=

4.8552 in. Cross-sectional area for premium class

=

Area based on reduced

Ddp

-

Area based on nominal ddp:

.It

d,,

=

2(4.8552)2--(4.276)2

=

4.1538in.*

4

Section modulus for premium class:

Dip

-

df

’=:(

D,

)=E(

4.8552

From Table 4-81,

PI

=

311,400 lb (using Equation

4-61),

(3,000)( 4.8552)( 4.1538)

(

4.1538)( 180,000)

[

0.2896 8.9526

=

260,500 lb

The reduction in the tensile load capacity of the drill pipe is 311,400

-

260,500

=

50,900 lb. That is about 17% of the tensile drill pipe resistance

calculated at the minimum yield strength in uniaxial state of stress. For practical

purposes, depending upon drilling conditions, a reasonable value of

safety

factor

should be applied.

During DST operations, the drill pipe may be affected by a combined effect

of collapse pressure and tensile load. For such a case,

or

(4-62)

Drill String: Composition and Design

747

(4-63)

where Pc

=

minimum collapse pressure resistance as specified by API in psi

PCc

=

corrected collapse pressure resistance for effect of tension in psi

Ym

=

minimal yield strength of pipe in psi

Substituting Equation 4-63 and Equation 455 into Equation 4-54 (note:

or

=

0,

z

=

0,

oe

=

Y,)

and solving PCc yields

or

P,,

=

(4-64)

(4-65)

Equation 4-65 indicates that increased tensile load results in decreased collapse

pressure resistance. The decrement of collapse pressure resistance during normal

DST operations is relatively small; nevertheless, under certain conditions, it may

be quite considerable.

Example

collapse of 1.1 for the DST conditions as below:

Determine if the drill pipe is strong enough to satisfy the safety factor on

Drill pipe: 4+-in., 16.6-lb/ft nominal weight, G-105 steel grade, class

2

Drilling fluid with a density of 12 lb/gal and drill pipe empty inside

Packer set at the depth of 8,500 ft

Tension load of 45,000 lb, applied to the drill pipe

From Table 4-84, the collapse pressure resistance in uniaxial state of stress,

Pc

-

6,010 psi. Reduced wall thickness for class

2

drill pipe

=

(0.65)(0.337)

=

0.219 in. Reduced

Ddp

for class

2

drill pipe

=

3.826

+

(2)(0.219)

=

4.264 in.

Reduced cross-sectional area of class

2

drill pipe equals:

IC

-(4.264)'--(3.826)'

=

2.783in.'

4

The axial tensile stress at packer level is

oz=L=

45

Oo0

16,170psi

2.783

748

Drilling and Well Completions

The corrected collapse pressure resistance according to Equation

4-65

is

Hydrostatic pressure of the drilling fluid behind the drill string at the packer

level is

P,

=

(0.052)(12)(8,500)

=

5,304

psi

Obtained safety factor

the drill pipe must not be run empty inside.

5,493/5,304

=

1.0356.

Since the obtained magnitude of safety factor

(1.03)

is less than desired

(l.l),

Tool

Joints

The heart of any drill pipe string is the threaded rotary shoulder connection

(Figure

4-133),

known as the tool joint. Today, the only

API

standard tool joint

is the weld-on joint shown at the bottom of Figure

4-133.

Tool joint dimensions for drill pipe grades

E,

X,

G

and

S

(recommended by

API)

are given in Table

4-84.

Selection of tool joints should be discussed with

the manufacturer. This is due to the fact that, up to the present time, there are

no fully reliable formulas for calculating load capacity of tool joints. It is

recommended that a tool joint be selected in such a manner that the torsional

load capacity of the tool joint and the drill pipe would be comparable. The

decision can be based on data specified in Tables

4-85

through

4-88.

Makeup Torque

of

Tool

Joints

The tool joint holds drill pipe together, and the shoulders (similar to drill

collars) form a metal-to-metal seal to avoid leakage. The tool joint threads are

designed to be made up with drilling fluid containing solids. Clearance must

be provided at the crest and root of threads in order to accommodate these

solids. Therefore, the shoulder is the only seal. To keep the shoulders together,

proper makeup torque

is

required.

However, makeup torque applied to the tool joint produces as axial preloading

in the pin and the box as well as

a

torsional stress.

In

particular, makeup torque induces a tensile state of stress within the pin

and compression stress in the box. Thus, when the tool joint is exposed to the

additional axial load due to the weight of the drill string suspended below the

joint, the load capacity of the tool joint is determined by the tensile strength

of the pin.

The magnitude of the makeup torque corresponding to the maximum load

capacity of the tool joint is called the recommended makeup torque.

Therefore, the actual torque applied to the drill string should not exceed

the recommended makeup torque; otherwise, the load capacity of the tool joint

is reduced.

The

API

recommended makeup torque for different types of tool joints and

classes of drill pipe is given in Table

4-89.

Drill String: Composition and Design

749

TAPERED

ELEVATOR

SHOULDER

(SEAT)

HEAT AFFECTED ZONE

(NOT

visieu ON

DRILL

UPSET DRILL

PIPE,

SEE

SEC.

B-

I

PAGE

9

HARDFACED

TONG AREA

AREA

RELIEF GROOVE

’

OR

PIN BASE RADIUS SHOULDER

MAKE

L

BREAK

\-SQUARE

(SEAT)

ELEVATOR

SHOULDER

LAST ENCAGED THREAD PIN

7

r-

LAST ENGAGED THREAD

-

BOX

LENGTH

OF

LENGTH OF

BOX

HARDFACING

IS

AN

OPTIONAL

FEATURE

Figure

4-133.

Tool

joint nomenclature

[30].

Heavy-Weight Drill Pipe

Heavy-weight drill pipe (with wall thicknesses

of

approximately

1

in.) is

frequently used for drilling vertical

and

directional holes (Figure

4134).

So

far,

there is no sound, consistent, engineering theory of drill string behavior while

(texf

continued

on

page

760)

750

Drilling and Well Completions

Table

4-84

Tool

Joint Dlmensions for Grade

E,

X,

G and

S

Drill Pipe

[30]

1

2

3 4

6

7

8

9 10 11 12 13 14

sheand

Nom.

Cnde'

'u

Iuld.

B.nl

TOW

Pia

Box

Corn-

Dia

Dim

Tor-

Dh

Dim

Dhof

Lcnrtb

Tong

Ton.

bind

of

oi

Bor

sional

of

Pln

oi

Pin8 Pin

amd

Td

SD.~

S~ua

Len.tb

at

El-

at

El-

II.tio.

snd

+1/64

Bm

Joint

2%

*Jc

of

vator

and

U~.ct

U~.et.

to

Box

Mu

Max Drill

Box

-l/IP

Shoulder

*1m

DRlLL

PIPE

TOOL JOINT

-

Tml

Joint

St,h

Wt.2

Daimstionl

Ib

Dcr

ti/6'

32

*%

PiDe

D

d

De

Lr

Lr.

L.

L

Dr. Dm

NC26(2%IF) 236EU 6.85 E75

3%'

1%* 31f 9 6

7

13

2*

2fk 1.10

X95 3%.

1%*

3tf 9 6

7

13

2A

2*

.87

G106 39b0 1%' 34% 9 6

7

13

21%

2fk

.79

NC31(2%IF) 2WEU 10.40

NC384

3% EU

9.60

NC38(3%IF) 3% EU

1360

16.60

NCIO(4FH) 3%EU 16.60

4 IU 14.00

NC46(4IF) 4 EU 14.00

4% IU 16.60

4%IEU

20.00

4% FHeo 4%IU 16.60

4wIEu 20.00

E75

x95

6105

S135

E75

x95

G1OS

S136

E75

X96

G1OS

S135

E75

x95

G105

S135

E75

X96

G106

S135

E75

x95

G105

S135

E75

x95

G105

S135

E75

x95

G105

,9136

E75

x95

G105

4%~

2%.

384

9% 6

8

14 3tr

3tr 1.03

4%.

2

3%t

9% 6

8

14 3&

3a .82

4%

1% 3%t

9.36 6 8

14 3I%

31%

.82

4%*

2

3%f 9% 6

8

14

SI%

311 -90

4%* 3 44 10~4

7

9% 16% 3% 346

.a

44% 11

7

9%

16% 3%

3% .93

::*

43% 11

7

9% 16% 3%

3%

.87

43%

11

7

9%

16%

3%

3% .86

5 5

;$

4Jf 11

7

9% 16% 3% 3%

.80

5

22.

434 11

7

9%

16% 3%

3%

.97

5

2&

4df 11

7

9%

16% 3%

3% .83

5

2%

41%

11

7

9% 16% 3%

3%

.90

6%

2%

5* 11%

7

10

5%:

2ti.

Sft

11%

7

10

6%

2ta

6t

11%

7

10

5%

2.h

5*

11%

7

10

5%

2

5* 11%

7

10

6* 3%* 598

11%

7

10

6*

3%* 511

11%

7

10

6' 3%.

638

11%

7

10

6*

3

631

11%

7

10

6'

3%.

53l

11%

7

10

6.

3 593

11%

7

10

6*

3 588

11%

7

10

6%

2%

589

11%

7

10

6*

3 533

11%

7

10

6%

2%

553

11%

7

10

6%

2%

538

11%

7

10

6%

2% 518

11%

7

10

68

3*

5lt

11

7

10

6'

2%

53a

11

7

10

6* 2%

53!3

11

7

10

6%

2%

53)

11

7

10

6*

3'

513

11

7

10

6'

2%

598

11

7

10

6*

2%

55#

11

7

10

17

3% 3%

a7

4*

4* 1.01

4*

4* .86

4tr

4tr .93

4%

4% 143

4%

4% 1.13

4%

4% 1.02

4%

4% .94

4%

4ia 1.09

4ft

4% 1.01

4tt

4%

.91

4th

4% 1.07

4it

4tt .96

4tt

4th .96

1.12

.92

4a 4tr

.a7

4tt 4th

ai

4th 4it .ai

4"::

t::

1.02

2:

1;

ai

4tt 4% .95

4tt

4th .96

4tt

4tt .86

~ ~~

*Denote.

standard

OD

or

standard ID.

**Ob.olcrecnt connection.

'The

twl

joint designation

(Col.

1)

indieate8 the

I&

and style

of

the applicable connection.

2Nominal weights.

thread.

and couplings.

(Col.

9)

an

8hOWn

for

the pnrpow

of

identification in ordering.

sTbe inside diameter

(Col.

6)

does

not apply to

box

members. which

am

optional with the mannfactursr.

rlcngth

of

pin thread

redneed

to

S%

inches

(%

inch

short)

to

accommodate

3

inch

ID.

NOTE

1:

Neck

diameters

(Dn

Q

k)

and inside diameters (d)

of

tool joints

prim

to welding are

at

mantlfscturer's

option. The above table spzcifies finished dimension.

after

final machining

of

the assembly.

NOTE

2:

Appendix

A

contain. more.dimensions

of

ohsoleacent connections and

for

square elevator shonlden.

NOTE

3:

No torsional ratio

(tool

Joint pin

to

drill pipe) less than

0.80

is

shown. In partictllar

areas,

tool

joints

&v-

ing much smaller torsional ylelds may prove to

be

adequate.

Drill String: Composition and Design

751

Table

4-84

(continued)

1

2 34 5

6

7

8

9 10

11

12 13 14

--

TOOL

JOINT

7

DRILL

PIPE

--

---

Sirrand

Nom.

Gnrde-

0ut.Y~

Inside

Bed

Total

Box

chn-

Di.

Tor-

Dis

Diu

Disd

lannh

Tons

s~.-

bind

01

dBox

swnd

of

Pin3

Pinand

Tml

SD~E.

ZX

lrnnh

at

Eie

st

Elc

Ratio.

Box

-113ZShou1d~1.

Pm

D

d

DP

LP

LP.

L,

L

Des

Dm

StYl.

\VLZ

Ib

-2

TOd

J0l"t

D..ip".tio"l

fl

and

fl164

Box

Joint

of

and

Pan

Umet.

-.for

Umt.

vamr

10

':t

?

Y,

PiM

Box

Mnr

Max

Drill

ZI/SY

*I164

EO(4WIF)

4%EU

16.60

E75

636*

3%* 51% 11%

7

10 17

5

1.23

X95

6%*

3%.

5%f 11%

7

10 17

5

.97

G105

6%'

3%.

5%: 11%

10

17

5 5

.38

S135

6%'

3% 5%1 11%

,

10 17

5

.81

4%

EU

20.00 E75

6%*

3%. 54% 11%

I

10 17 5 5 1.02

X95

6%'

3%

5%E

11%

7

10

17

5 5 .96

G105

6%-

3%

5%f

11%

I

10 17 5 5

36

S135

6%

3

5%f

11%

'I

10 17

5

.87

5

IEU

19.50 E75

6%'

3%'

51%

11%

7

10 17 5% 5% .92

X95

6%.

3%

5@$

11%

7

10 17 5% 5%

.86

G105

6%

3%

5%Y 11%

7

10 17 5% 5% .89

5135

6%

2%

51t

11%

7

10 17 5% 5%

.86

5

IEU

25.60

E76

6%'

3%

51t 11%

7

10

17

5%

.86

X95

6%

3

50f 11%

7

10

17 5% 5%

.86

G105

6%

2% 5$4 11%

7

10

17

5%

6%

.87

5%

FH-'

5

IEU

19.50 E75

7'

3%

68:

13

8

10 18

5% 5%

1.53

X95

7*

3%

618

13

8

10 18

5%

5% 1.21

GI05

7*

3%

632

13

8

10 18 5% 5%

1.09

Si35

7%

3%

603

13

8

10

18

5%

5% .98

5

IEU

25.60 E75

7'

3%

63:

13

8

10

18

5%

5% 1.21

X95

7'

3% 611

13

8

10 18 5% 5%

.95

G106

7%

3%

61:

13

8

10

18 5% 5%

.99

S135

7%

3%

6::

13

8

10

18

5%

.83

5%

IEU

21.90 E75 7' 4

63;

13

8

10 18 5fl 5ft

1.11

X95

lo

3%

611

13

8

10

18

5tl 51t .98

G105

7%

3%

61:

13

8

10 18 5tt

5tt

1.02

S135

7%

3

72.

13

8

10

18 5th 5fh .96

5HIEU

24.70

E75

IC

4*

6:;

13

8

10

18

5ft

5fb .99

X96 7%

3%

631

13

8

10

18

5t3.

5th 1.01

G105

7%

3%

603

13

8

10

18

5th 5fh .92

5135

7%

3

73!1

13

8

10 18 5tt 5th

.86

~

Wenotea

standard

OD

or standard

ID.

"Obsolexent connection.

'The tool joint designation

(el.

1)

indiutcs the sire and rtyle

of

the appliuble eonneetion:

2)l'ominsd weights, thread. and eoIIplings.

(Col.

8)

are

shown for the

PUrpI

of

identieutlon in ordering.

>The inside

diameter

(Col.

6)

don not apply

to

box

memben,

which

-1Lcngth

of

thread

mdueed

to

S%

inches

(34

inch ahort)

to

Meommod+

S

inch

ID.

NOTE

1:

Neck diimcten

(Dn

&,

Dn)

and inside diameters (d)

o!

fool

joint.

prior

to

welding

are

st

mmulaeturer'a

option. The

above

tabla

spsifiea

fimshui

dimensions after

find

maehming

of

the assembly.

NOTE

2:

Appendix

H

eont.in.

mom

dimmaions

of

obsolescent

eonnectiona

and

for

wusre

elantor louiden.

NOTE

3:

No torsional ratio

(tool

joint pin

to

drill pipe)

lesa

then

0.80

is shown. In particuhr

.mu,

tool

joints

hmv-

in*

much

amrller

torsions1 yields

may

prove

to be

ndeguate.

optn0n.l with the manulactUTer.

Table

4-85

Selectlon Chart-Tool Joints Applied to Standard Weight Drill Pipe-Grade

E

[30]

DRILL

PIPE

DATA

-

TOOL

JOINT ATTACHED

TOOL

JOINT

DATA

MECHANICAL

PROPERTIES

Nom.

Size

2 318

2

7D

3 1/2

4

4 1/2

5

111

6

SA

upwt

Nom.

Nj.

Wt.

nJm

665

10.40

13.30

14.00

16.60

1950

21.90

25.20

Wl.

1.D.

lb/rt(I)

in.

6.75

1.815

6.87

7.00

10.29 2.151

11.20

10.37

10.82

10.57

1053

14.06 2.764

1351

13.86

15.13

3.340

14.29

is50

15.56

15.07

11.94 3.826

17.70

16.66

17.94

17.64

17.22

20.99 4.276

n.94 4.118

27.14

5.965

TYPC

IU

EU

IU

EU

IU

EU

IU

1U

EU

PU

IU

EU

IEU

IU

hX.

O.D.

Drift

in.

Dia

2112 1.312

29/16 1.627

3 1.438

3 1.812

3 1.688

3 3/16 1.963

3 3/16 1.006

3

11/16

2.313

3 11/16 2.000

3118 2.446

3 7/8 2.446

43/16 2688

43/16 2.438

43/16 2.688

4 112 3.125

4

llll6

3.121

4 11/16 2.875

4 11/16 2.562

4llll6 3.125

5 3.625

5 3.125

5

ID

3.625

5

iim

3675

Coni.

PAC

O.H.

NC2MI.F.)

PAC

E.H.

NC26(S.H.)

NC3I(I.F.)

O.H.

SL4i90

E.H.

NCJI(S.H.)

NC38(I.F.)

on.

NC4WF.H.)

S.H.

H90

NC4Ml.F.)

O.H.

NC46(E.H.)

R.H.

NC38(S.H.)

ti90

NCSO(1.F.)

OR.

NCSMEH.)

FM.

O.D.

in.

2 718

3 114

3 3D

3

ID

4 I/4

3 3/8

4

1/8

3 7/8

3

7/8

4 314

4

1/8

4 314

5

114

4

518

5

112

6

5 i/2

6

5

6

6 3/8

5

7/8

6 318

1

Toq

Spcc

Tensile

Yield

in.

Ib

I.D.

in.

Box

138 7

1314 7

I314 7

I1/2

8

17/8

8

I3/4

8

2118

8

25/32

8

25/32

8

27/16 9

112

21/8

8

112

2ll/l6 9 I12

2 11/16 9 112

2 13/16

10

29/16

91R

2 13/16

IO

3 li4

10

3 l/4

10

3 114

10

3

10

211/16 9 112

3 114

10

3

3/4

IO

33/4

10

3314

IO

4

10

PipespeU)

6 138220

6 214340

7

271570

61/2 271570

7 271570

7

msxo

6 112

285360

7 285360

7

285360

7 285360

7 330560

6 1/2 330560

7

330560

7

330560

7 330560

7 395600

8

437120

Tool

Joint

(3)

262ooo

287280

323760

269410

516840

323760

459120

345840

384600

584880

459120

602160

560040

721440

525840

913680

918960

760080

918960

976440

601880

938280

958800

718080

958800

1265880

Ta~io~l

Yidd

ft-lb

6240

11530

I85

20

18520

23250

30750

30150

30750

41090

50620

Td

Joint

(5)

5200

6400

6800

5800

13400

6800

I2000

8600

11800

17300

12000

18700

14900

24000

I5400

35520

34100

26800

34100

34600

18700

37400

37900

27400

37900

55700

6

314 4.875

F.H.

8

.

...

.

5

14112 9112 489460 1448880 70550 73000

Tool

Joint

Plus

'29.4'ofDrlO

Plpc.

Tensile

Yield Strenith

of

the

Tool

Joint

u

bwd

on

110#00

pi

Ybld and

the

Crw

Scctiond

Are.

at

the

Root

of

the

Thread

r/8

inch

horn

the Shoulder.

Toniond

Yield Strenph

of

the

Drill

Pip

is

Baud

on

n

ShDu

Strength

of

S7.7Xof

the Minimum Yield Strength.

Todonal

Ybld Strength

of

the

Tml

Joint B.sed

on

Tande

Yield Strongth

of

the

and

Compreuive

Ywld Strength

of

the

Box

-

Lowest

Value

Prevailing.

2

Tenlle

Ybld Stnnith

of

DrlU

Pip B-d

on

75,000

psi.

4

u1

Nl

6

a

Table

4-86

Selection

Chart-Tool

Jolnts

Applied

to Lightwelght

Drill Plpe-Grade

E

[30]

DRlU

PIPE

DATA

-

TOOL

JOlM

ATTAcHeD

MOL

JOINT

DATA

MECHANICAL PROPERTIES

Nom.

Wt.

b/lt

4.85

6.85

9.50

11.85

13.75

W*

Wt.

I.D.

blrt

(1)

in.

Type

5.15 1.995

EU

4.94

EO

4.87

EU

5.09

EU

7.33 2.441

EU

6.91

EU

6.91

EU

7.25

EU

10.39 2.992

EU

10.12

EU

9.95

EU

10.2s

EU

13.09 3.476

IU

13.13

EU

12.16

EU

13.03

EU

15.24 3.958

IU

14.98

EU

14.10

EO

14.90

EU

M.X.

O.D.

Drift

in.

Dn

Conn.

2

9/16 1.688

NC26(I.F.)

29/16

1.850

SL-H'H)

29/16 1.807

OH.

2 9/16 1.807

W.O.

3

3/16

2.063 NC31(l.F.)

3 3/16

2.296 S.L.-H9O

33/16 2.253

OH.

3 3/16 2.253

W.O.

3 7/8

2.563 NC38U.F.)

3 718 2.847 S.L.490

3 718 2.804 O.H.

3 718 2.804

W.O.

43/16 2.688

H90

4 112

3.125

NC46U.F.)

4 112 3.287 O.H.

4 112

3.287

W.O.

4

11/16 3.125 H90

5

3.625 NC5WI.F.)

5 3.770

O.H.

5

3.770

W.O.

09.

in.

3 3/8

3 114

3 118

3 318

4

1/8

3 718

3 314

3 78

4 314

4

518

4

112

4 3/4

5 112

5

314

5

114

5

314

6

I/8

5

314

6

18

19.

in.

1314

1.995

2

118

2.441

2 7/16

2 11/16

2.992

3

2

13/16

3

114

3 15/32

3 7/16

3 l/4

3 314

3 31/32

3 718

Tdc

Yidd

TW*Od

Ydd

To?

sP=

in.

Ib

Mb

BOX

7

8

9 112

9

1/2

10

IO

10

Tool

Pipe(2) Joint

(3)

6

91820 323760

6 97820 204550

6 97820 206400

6' 97820 205920

6' 135900 459120

6 135900 259180

6 135900 224040

6' 135900 289080

7'

194260 602160

6 112194260 370970

7

194260 392280

7'

194260 434400

7 230750 913680

7. 230750 918960

7

230750 621960

7'

230750 801120

7

270030 938280

7. 270030 958920

7 270030 559440

7' 270030 868920

Pipe

(4)

4760

8070

14120

19440

25860

Tool

Joint

(5)

6800

5500

4400

4500

12000

7600

5800

7500

18700

13200

11800

I3400

3s500

34100

22100

29300

37400

37900

21

100

34100

*If

weight

is

of

paramount importance, these connections

can

be supplied with

a

smaller

O.D.

or shorter tong space on box and pin,

or

a

combination

of

the two

to

afford mix-

imum

weight

redudon without sacrificing

safety

in

the

joint. However, where possible, the manufacturers recommend ordering the joints shown to obtain the niaximum economi-

al

tool

joint service.

Otha

tool jointrircs

to

accommodate

rpecirl

situations can be furnished

on

request.

1

Td

Joint

Plus

29.4'

of

Drill

Pipe.

2

Tensile Yield Stmn(th

of

Drill

Pipe

Baed

on

75,000

psi.

3

Tensile Yield Strcnith

of

the Tool Joint

is

based

on

I20,OOO

Psi

Yield and the Croa Sectional

Area

a1

the Root

of

the Thread

51s

inch

from the Shoulder.

4

Torrional Yield Strength

of

the Drill Pipe ia Baaed

on

a

Shear Strenglh of

5l.lqbof

the Minimum Yield Strength.

5

Tonionsl Yield Strenglh ofthe

Tool

Joint Bawd

on

Tensile Yleld Strength of the

and Compressive Yield Strength

of

the

Box

-

owe st Value

Prevailing.

8

g.

3

a

0

E.

3

w

3

a

U

a

5'

1

-l

rJl

rp

Table

4-87

Selection

Chart-Tool

Joints Applied to Heavy-Weight Drill Pipe-Grade

E

[30]

Y

e

MECHANICAL

PROPERTIES

DRILL

PIPE

DATA

-

TOOL

JOINT

ATTACHED

TOOL

JOINT

DATA

Nom.

Size

3 112

4

4 112

5

5 112

Nom.

Adj.

Wt. Wt.

Ib/ft lblft

(1)

1550

15.70t

20.00

22.82

25.60

24.70

16.42

16.99

17.30

17.43

21.73

22.33

2453

24.53

2453

24.5 4

27.17

28.08

26.86

1.D.

in.

2.602

3.240

3.640

3.500

4.00

4.670

Max.

O.D.

Drift

Type

in.

Dia

EU 3 718 2.414

1U

4 3/16 2.562

1U 4 3/16 2.688

EU 4 112 3.052

IEU

4 11/16 2.875

IEU

4 11116 2.875

IEU 4 11116 2.875

EU 5

3.452

IEU 4 11/16

2.875

IEU

4 11/16 2.875

IEU

4 11/16 2.875

EU

5

118

3.312

IEU

5

118 3.375

IEU 5 118

3.375

IEU 5 11/16

3.875

Cann.

NC38(1.F.)

NCQO(F.H.)

H90

NC46U.F.)

NC46(E.H.)

F.H.

H90

NC5II.F.)

NC46 (E.H.)

F.H.

NCSO (1.F.)

NCSO(E.H.)

5

Il2F.H.

F.H.

H-90

O.D.

in.

5

5 114

5 112

6

6 318

6

6 318

7

19.

in.

2 9/16

2 11116

2 13116

3 114

3

3 314

3

3 112

4

Tong

Spice Tensile Yield

in.

lb

Tod

Box

Pipe(2)

Joint

(3)

9

112

7 322780 663550

10

7

324150 791620

10

7

324150 913680

10 7

324150 918960

10

7

10

7

10

7

10

7

10

7

10 7

10

7

IO

7

412360

4 12360

412360

47 I240

471240

47 1240

1066030

976130

1085380

95800

1066030

976130

1085380

958800

10

7

53180 1128960

10

8

530180 1268540

IO

8

497220 1265880

w

ti'

Toniod

Yield

ft-lb

09

P

Pipe

(4)

Joint

Tool

(5)

e.

5

21050

25760

36840

40910

20600

-

6

39400

g.

25900

35500

34

100

a_

44600

2

CD

34600

37900

39400

34600

44600

37900

52160 44600

52160 59000

56470 55700

?Not

APl

weight

I

Tool

Joint Plus

29.4'of

DriU

Pspe.

2

Tensile Yield Strength

of

Drill

Pipe Bad

on

75,000

psi.

3

Tensile Yield Strength

of

the Tool Joint

is

based

on

120,000

psi

Yield and the

Cros

Sectional

Area

at the

Root

of

the Thread

518

inch from the Shoulder.

4

Torsional

Yield Strength

of

the

Drill

Pipe ir Based

on

a

Shear Strength

of

57.7%of

the Minimum Yield Strength.

Torsional Yield Strength

of

the Tool Joint Bared

on

Tensile Yield Strength

of

the

md

Compressive Yield Strength

of

the

Box

-

Lomst

Valw

Prevailing.

Lyons W.C. (ed.). Standard handbook of petroleum and natural gas engineering.2001- Volume 1

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