U.S. patent number 3,709,306 [Application Number 05/115,571] was granted by the patent office on 1973-01-09 for threaded connector for impact devices.
This patent grant is currently assigned to Baker Oil Tools, Inc.. Invention is credited to Alfred R. Curington.
United States Patent |
3,709,306 |
Curington |
January 9, 1973 |
THREADED CONNECTOR FOR IMPACT DEVICES
Abstract
An impacting apparatus in which a threaded connection is
provided between an anvil and a drill bit connected thereto, a
malleable member located between the anvil and bit threads insuring
a more uniform load distribution over the thread surfaces, the
blows on the anvil being transmitted directly to the bit without
passing through the malleable member.
Inventors: |
Curington; Alfred R. (Houston,
TX) |
Assignee: |
Baker Oil Tools, Inc. (City of
Commerce, CA)
|
Family
ID: |
22362193 |
Appl.
No.: |
05/115,571 |
Filed: |
February 16, 1971 |
Current U.S.
Class: |
173/132; 173/80;
173/78 |
Current CPC
Class: |
E21B
4/06 (20130101); E21B 17/0426 (20130101) |
Current International
Class: |
E21B
17/042 (20060101); E21B 17/02 (20060101); E21B
4/00 (20060101); E21B 4/06 (20060101); E21b
001/06 () |
Field of
Search: |
;173/131,132
;175/320,409,414-420 ;287/125 ;285/338,355,357,422 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Purser; Ernest R.
Claims
I claim:
1. In percussive drilling apparatus: a first impact member adapted
to receive an impact blow; means for delivering repeated impact
blows to said first impact member; a second impact member having
means engaging the first impact member to receive the blow from the
first impact member; and connecting means for threadedly securing
said members to each other comprising a box having internal
threads, a pin within said box and having external threads
conforming to said internal threads, and a malleable sleeve between
said pin and box threads in intimate contact with said pin and box
threads to transmit load therebetween.
2. In drilling apparatus as defined in claim 1; said pin and box
threads being straight threads.
3. In drilling apparatus as defined in claim 1; said pin and box
threads being straight threads of divided pitch.
4. In drilling apparatus as defined in claim 1; the material of
said malleable sleeve being copper.
5. In drilling apparatus as defined in claim 1; said malleable
sleeve being a plating on at least one of said pin and box
threads.
6. In drilling apparatus as defined in claim 1; said pin and box
threads being straight threads; the material of said malleable
sleeve being copper.
7. In percussive drilling apparatus: an anvil member adapted to
receive an impact blow; means for delivering repeated impact blows
to said anvil member; a bit member having means engaging said anvil
member to receive the blow therefrom; said bit member having an end
face for impacting against the bottom of a bore hole; and a
threaded connection between said anvil and bit members comprising a
box on one of said members having internal threads, a pin on the
other of said members within said box and having external threads
conforming to said internal threads, and a malleable sleeve between
said pin and box threads in intimate contact with said pin and box
threads to transmit load therebetween.
8. In drilling apparatus as defined in claim 7; said pin and box
threads being straight threads.
9. In drilling apparatus as defined in claim 7; said pin and box
threads being straight threads of divided pitch.
10. In drilling apparatus as defined in claim 7; said box being on
said bit member and said pin being on said anvil member.
11. In drilling apparatus as defined in claim 7; said box being on
said bit member and said pin being on said anvil member; said pin
and box threads being straight threads.
12. In drilling apparatus as defined in claim 7; said box being on
said bit member and said pin being on said anvil member; the
engagement between said anvil and bit members being between the
lower end of said anvil member and the lower end of said box.
13. In drilling apparatus as defined in claim 7; the material of
said malleable sleeve being copper.
14. In percussive drilling apparatus: a first rod member adapted to
receive an impact blow; means for delivering repeated impact blows
to said first rod member; a second rod member in endwise engagement
with said first rod member to receive the blow therefrom; and
connecting means securing said members together comprising a
coupling sleeve having internal threads and surrounding the
adjacent portions of said members, said adjacent portions having
external threads conforming to the internal threads of said
coupling sleeve, and malleable sleeve means between and in intimate
contact with said internal threads and the external threads of said
adjacent portions to transmit load therebetween.
15. In drilling apparatus as defined in claim 14; said internal and
external threads being straight threads.
16. In drilling apparatus as defined in claim 14; said internal and
external threads being straight threads; the material of said
malleable sleeve means being copper.
17. In drilling apparatus as defined in claim 14; said internal and
external threads being straight threads; said malleable sleeve
means being a plating on at least one of said internal and external
threads.
18. A percussive drill bit having a thread portion adapted to be
threadedly secured to an impact anvil, said bit having an end face
for impacting against the bottom of a bore hole and a face adapted
to be engaged by the impact anvil to receive blows therefrom, and a
malleable sleeve on said thread portion in intimate surface contact
with the threads of such portion.
19. A percussive drill bit as defined in claim 18; said thread
portion being an internal thread portion.
20. A percussive drill bit as defined in claim 18; said malleable
sleeve being a copper sleeve.
21. A percussive drill bit as defined in claim 18; said thread
portion being an internal portion; said malleable sleeve being a
copper sleeve.
Description
The present invention relates to percussive drilling apparatus, and
more particularly to apparatus embodying threaded connectors or
couplings in the path of transmission between the percussive source
and the drill bit.
In percussive anvil and bit devices, such as used in air hammers,
the anvil and bit have been made integral with one another, except
in small hand-held machines, involving substantial cost and
relatively low effective life of the anvil portion, since it is
discarded with the worn or damaged bit portion of the combination.
With the view of making the anvil reusable, attempts have been made
at threadedly connecting the bit to the anvil, enabling the worn
bit to be disconnected from the anvil and a new or replacement bit
threadedly secured to the latter. Such attempts have been
unsuccessful since breakage occurs at the threaded region, which
may be due to fatigue failure. Polishing, rolling, shock peening,
nitriding, and other methods of improving the finish of the
threads, or inducing compressive stresses in the threads, have been
tried in an effort to overcome the breakage difficulty, but without
success.
It is believed that prior failures are caused by imperfect thread
fits, and not necessarily by imperfect threads. Since it is not
possible, as a practical matter, to produce mating pin and box
threads that match perfectly, initial contact between the threads
occurs at only a few points. During drilling, the hammering action
applied to the threads is concentrated at those few points,
effecting deformation at such points, with resultant very high
localized stresses, fatigue cracks occuring at the points of high
stress. Even with a theoretically perfect thread form, the same
undesirable result would be achieved, since the difference in pitch
diameters between the box and pin threads required for assembly
causes the thread forms or profiles to be different.
By virtue of the present invention, a threaded connection is
provided in the path of impact blow transmission between a
percussive source and a drill bit, as between the anvil portion and
bit of a percussive drilling apparatus, which virtually eliminates
fatigue failures at the threaded region, thereby resulting in a
threaded connection having a greatly increased useful life,
enabling worn bits to be replaced without the necessity for also
replacing other parts or portions of the apparatus that are still
in operable condition.
Additionally, a threaded connection is provided in which the loads
are distributed more uniformly over the thread surfaces, thereby
eliminating high localized stresses which initiate fatigue cracks
and failures. Uniform load distribution occurs despite some
imperfections or mismatching of the interfitting threads.
Another object of the invention is to provide a threaded connection
in which more uniform distribution of load over the threaded
surfaces is achieved, with the interfitting threads being of
divided pitch; that is, multiple start threads.
In general, the objectives of the invention are achieved by placing
a ductile material between the mating thread surfaces, such
material deforming or yielding under load, thereby causing
substantially the full surface areas of the threaded surfaces to
share the load and preventing concentration of the load at a few
points of the threads. The ductile material, such as a malleable
metal insert, can be either loosely inserted or physically attached
to the pin or box threads, preventing pressure at any point in the
threaded connection from exceeding the yield strength of the
ductile material, thereby eliminating any high uneven loading of
the thread surface that might exceed the yield strength of the pin
or box material, which could produce local failure or cracks and
ultimate failure of the threaded connection.
This invention possesses many other advantages, and has other
objects which may be made more clearly apparent from a
consideration of several forms in which it may be embodied. Such
forms are shown in the drawings accompanying and forming part of
the present specification. These forms will now be described in
detail for the purpose of illustrating the general principles of
the invention; but it is to be understood that such detailed
description is not to be taken in a limiting sense.
Referring to the drawings:
FIGS. 1a and 1b together constitute a longitudinal section through
an apparatus embodying the invention disposed in a bore hole, FIG.
1b being a lower continuation of FIG. 1a;
FIG. 2 is an enlarged fragmentary section taken in the encircled
region 2 of FIG. 1b;
FIG. 3 is an enlarged cross-section taken along the line 3--3 on
FIG. 1b;
FIG. 4 is a side elevational and longitudinal sectional view of
another embodiment of the invention;
FIG. 5 is an enlarged fragmentary section taken in the region 5 of
FIG. 4;
FIG. 6 is a longitudinal section through an apparatus for deforming
and securing a malleable sleeve in the threaded box portion of a
percussive drilling bit; and
FIG. 7 is a view similar to FIG. 6 illustrating the sleeve pressed
into the bit threads.
The invention is illustrated in the drawings as applied to a
downhole drilling hammer A connected to the lower end of a string
of drill pipe B extending to a drilling rig (not shown) at the top
of a bore hole C, and by means of which the apparatus and a drill
bit D connected to its lower end are rotated while compressed air
or any other suitable fluid medium is pumped down the drill pipe
for operating the apparatus. The drill bit D is of any suitable
type, and may have its end face tipped with tungsten carbide (not
shown) for impacting against the bottom F of the bore hole while
the apparatus A and bit D are being rotated, to insure drilling
action against the full area of the bottom of the hole as a result
of an impacting action imparted to an anvil 10 threadedly connected
to the drill bit.
The drilling hammer apparatus A includes an outer elongate housing
11, the upper end of which is threadedly connected to an upper sub
12 having an upper threaded box 13 for attachment to the lower pin
14 of an adjacent drill pipe section B. The lower end of the
tubular housing is threadedly secured to a lower sub 15 surrounding
the upper portion of the anvil 10. This sub has drive keys 16
fitting in elongate grooves or keyways 19 in the anvil 10.
Accordingly, turning effort or drilling torque can be transmitted
from the drill pipe B through the upper sub 12 and housing 11 to
the lower sub 15, and from the lower sub to the anvil 10, which can
move longitudinally within and relative to the lower sub and
housing 11, as described hereinbelow.
The upper sub 12 terminates in a head 20 closing the lower end of a
central passage 21 through the upper sub, and which forms the upper
head of a cylinder 22 that includes a cylinder sleeve 23, the upper
end of which is threadedly secured to the head 20, and which
extends downwardly in the housing, its lower end 24 terminating a
predetermined distance above the upper end of the lower sub 15.
This cylinder sleeve has an intermediate external flange or head 25
fitting closely within the housing, this flange carrying a suitable
side seal ring 26 sealingly engaging the inner wall 27 of the
housing. The cylinder sleeve has a reduced diameter above and below
the flange, providing an upper high pressure annular passage 28
between it and the housing, and also a lower low pressure or
exhaust annular passage 29 between the lower portion of the
cylinder sleeve and the inner wall of the housing. This low
pressure passage 29 opens into the space 30 below the sleeve 23,
communicating through inlet ports 31 in the anvil with a central
passage 32 in the latter that communicates with a companion passage
33 in the drill bit. The air or other fluid in the passage 33 is
capable of passing through the bit passages or nozzles 34, jetting
against the bottom of the hole, so as to clean the hole bottom F,
as well as the bit itself, of cuttings, and to flush the cuttings
upwardly around the bit D and drilling apparatus A and through the
annular space between the drill pipe and wall of the bore hole to
the top of the latter.
The anvil 10 terminates in an upper imperforate impact head 35
fitting snugly, but slidably, within the lower end of the cylinder
sleeve 23. The impact head of the anvil is adapted to be struck by
an elongate hammer piston 36 reciprocable within the cylinder
sleeve 23, this piston having a longitudinal impact passage 37
opening through its upper end and communicating through a lower
exhaust port 38 with an external circumferential exhaust piston
groove 39. The piston also is provided with a hammer return
longitudinal passage 40, opening through its lower end and
communicating at the upper portion of the piston with an inlet port
41 opening into an external peripheral piston groove 42.
The cylinder sleeve 23 has one or more lower exhaust ports 43
extending between the low pressure annular passage 29 and the lower
interior portion of the cylinder sleeve, and also has one or more
inlet ports 44 in the upper portion of the cylinder sleeve
establishing communication between the high pressure annular
passage 28 and the upper portion of the interior of the cylinder
sleeve. The longitudinal distance between the lower piston exhaust
port 38 and the upper piston inlet port 41 is equal to the
longitudinal distance between the inlet ports 44 and the exhaust
ports 43. The exhaust ports 43 are so related to the upper end of
the anvil 10 when the anvil is fully telescoped upwardly within the
housing 11 that the lower end of the hammer piston 36 is engaging
the anvil when the inlet ports 44 are aligned with the upper piston
groove 42 and the exhaust ports 43 are aligned with the exhaust
groove 39 at the lower portion of the piston, as disclosed in FIGS.
1a and 1b. With the piston 36 in this lower position, high pressure
air can flow from the high pressure annulus 28 through the cylinder
ports 44, groove 42 and piston inlet port 41 into the hammer return
passage 40, passing to the lower end of the piston and exerting an
upward force on the piston to shift it upwardly toward the upper
cylinder head 20. At the same time, the air in the cylinder space
46 above the piston can pass through the impact passage 37 and
through the exhaust port 38, exhaust groove 39 and cylinder exhaust
ports 43 into the low pressure annular passage 29, flowing
downwardly therearound and through the anvil inlet ports 31 into
its central passage 32 for discharge through the bit D.
The upper peripheral groove 42 is formed in an upper land 47 of the
piston that makes a close sliding fit with the inner wall of the
cylinder sleeve 23. On opposite sides of the groove 42, the land is
provided with a plurality of circumferential labyrinth seal grooves
48 to inhibit leakage of fluid between the periphery of the land
and the inner wall of the cylinder sleeve. Similarly, the lower
exhaust groove 39 is provided in a lower land 49 that makes a close
sliding fit with the inner wall of the cylinder sleeve 23, this
land also having labyrinth seal grooves 50 on opposite sides of the
exhaust groove 39 for minimizing leakage of fluid between the lower
land and the inner wall of the cylinder sleeve. The piston has an
intermediate land 51 slidably and sealingly engaging the inner wall
of the cylinder and also provided with labyrinth seal grooves 52 in
its periphery to prevent leakage of fluid between the land 51 and
the cylinder wall. The piston also has a reduced diameter portion
53 between the upper and intermediate lands 47, 51, to define with
the cylinder wall an elongate high pressure circumferential groove
54 communicating with a side port 55 in the piston that extends
from the lower portion of the groove 54 to the impact passage 37.
When the piston 36 is in an elevated position, the high pressure
groove 54 is in communication with the inlet ports 44 through the
cylinder sleeve, so that high pressure air can flow through the
sleeve ports 44 and high pressure groove 54 through the inlet port
55 into the impact passage 37 and into the cylinder space 46 above
the piston for the purpose of driving the hammer piston 36
downwardly to strike an impact blow upon the lower anvil 10.
The lower side 70 of the upper peripheral groove 42 will shut off
fluid flow through the ports 44 and into the hammer return passage
40 at the same time that the lower side 71 of the lower peripheral
exhaust groove 39 shuts off the lower exhaust ports 43. When this
occurs, high pressure air can no longer flow through the hammer
return passage 40 to the lower end of the cylinder sleeve to
elevate the piston 36, nor can any further air in the cylinder
above the piston flow through the impact passage 37 and exhaust
ports 38, 43. In addition, the lower end 72 of the upper land 47 at
the upper end of the elongate high pressure piston groove 54 will
open the inlet ports 44 at the same time that the lower end 73 of
the lower land 49 opens the exhaust ports 43 as a result of
elevation of the piston in the cylinder sleeve. Thus, there will be
communication of high pressure air with the high pressure groove 54
communicating with the impact passage 37 simultaneously with
communication of the air under pressure below the piston 36 with
the cylinder sleeve exhaust ports 43.
From the foregoing description, it will be noted that the upper
inlet ports 44 and the lower exhaust ports 43 are simultaneously
shut off from communication with the hammer return passage 40 and
the impact passage 37, and that they are brought into simultaneous
communication with the impact passage 37 and the hammer return
passage 40 during upward travel of the piston 36 in the cylinder
22. The piston can continue travelling upwardly in the cylinder
sleeve 23, but in view of the elongate high pressure passage 54
surrounding the piston, and the disposition of the lower end of the
piston above the exhaust ports 43, the introduction of high
pressure air into the cylinder space 46 above the piston and the
exhaust of air from below the piston to the low pressure annular
passage 29 continues.
In the operation of the drilling hammer, the drill bit D is secured
to its anvil 10 and the drill pipe B to its upper end, whereupon it
is lowered in the bore hole C. When the drill bit contacts the
bottom F of the hole, it comes to rest and the apparatus A is
shifted downwardly along the anvil 10 until the lower end 15a of
the sub 15 engages the upper end 60 of the bit D, permitting a
suitable amount of drilling weight to be imposed upon the apparatus
and the bit to retain the latter in contact with the hole bottom.
The drill pipe B is then rotated to rotate the bit D and compressed
air at an appropriate pressure pumped down the drill pipe and into
the apparatus A. At the beginning of the impacting operation of the
apparatus, the hammer piston 36 will be disposed in its lower
position, as illustrated in FIGS. 1a, 1b, resting upon the upper
end 35 of the anvil 10 which is then disposed in sealing relation
within the lower end of the cylinder sleeve 23. With the piston in
this position, the impact passage 37 communicates with the exhaust
ports 43; whereas, the hammer return or elevating passage 40
communicates with the high pressure ports 44. Air under pressure
then flows from the sub passage 21 through its side ports 21a into
the high pressure annulus 28 and the piston return passage 40 to
the lower end of the piston, acting upon the full cross-sectional
area of the piston to shift it upwardly within the cylinder sleeve
23. As the piston is moved upwardly by the compressed air, the
upper land 47 and its shoulder 70 shut off flow of the fluid
through the inlet ports 44 to the return passage 40 simultaneously
with the shutting off of flow of fluid by the lower land 49 and its
shoulder 71 from the cylinder space 46 above the piston 36 through
the impact passage 37 and through the exhaust ports 43. At this
time, the high pressure air or other gas below the piston 36 has
imparted a certain amount of kinetic energy to the piston, the high
pressure air below the piston expanding to continue the upward
movement of the piston within the cylinder sleeve 23 and
compressing the low pressure air in the cylinder space 46 above the
piston. The piston will continue to rise in the cylinder as a
result of expansion of the high pressure air therebelow until the
lower end 73 of the lower piston land 49 opens the exhaust ports
43, the inlet ports 44 being opened at the same instant, by
movement of the shoulder 72 above the ports 44, to communication
with the high pressure piston groove 54 that communicates with the
impact passage 37. During expansion of the high pressure gas below
the piston, additional kinetic energy is imparted to the piston,
the high pressure air below the piston then exhausting from below
the piston through the exhaust ports 43 into the low pressure
annulus passage 29, from which it can flow through the anvil ports
31 and through the central anvil passage 32 and through the drill
bit to flush the cuttings from the bottom of the hole and upwardly
around the bit and the annulus surrounding the drill pipe to the
top of the bore hole. The piston 36 continues moving upwardly in
the cylinder until its kinetic energy is overcome by the high
pressure air flowing through the impact passage 37 and into the
cylinder space 46 above the piston. The air trapped above the
piston will have been compressed by the upward travel of the piston
in the cylinder 22, but on the return or down stroke of the piston
under the influence of high pressure air in the upper portion 46 of
the cylinder, the energy in the trapped air will be released and
assist in propelling the piston downwardly within the cylinder.
Such downward or power stroke of the piston will commence when the
compressed air in the cylinder above the piston equals the kinetic
energy of the ascending piston, reducing the kinetic energy and the
velocity of the piston to zero at the top of the stroke. At this
time, the piston will still be a short distance away from the upper
cylinder head 20 and will be prevented from impacting
thereagainst.
The high pressure air being fed into the cylinder space 46 above
the piston 36 then drives the piston downwardly on its power
stroke, such high pressure air being fed into the upper portion of
the cylinder until the lower end 72 of the upper land 47 closes the
inlet ports 44, which action will occur simultaneously with closing
of the exhaust ports 43 by the lower end 73 of the lower land.
However, the air pressure in the cylinder below the piston 36 is
then at the low value of that existing in the low pressure annular
passage 29, so that the piston can continue moving downwardly at
high velocity to impact against the upper end 35 of the anvil
10.
When the piston hammer 36 strikes the anvil, the exhaust ports 43
again communicate with the impact passage 37, allowing the
compressed air in the cylinder space above the piston to exhaust
into the low pressure annular passage 29 and then through the ports
31, anvil passage 32 and drill bit passage 33, 34 into the bore
hole C. At the same time, the inlet ports 44 in the sleeve 23 are
again communicating with the piston return passage 40 so that high
pressure air is again conducted through such passage into the
cylinder sleeve 23 below the piston to again elevate the piston 36,
resulting in repetition of the cycle of operation of the
equipment.
The general drilling hammer arrangement illustrated in the drawings
forms the subject matter of applicant's application for "Down-Hole
Drilling Hammer," Ser. No. 863,988, filed Oct. 6, 1969, now U.S.
Pat. No. 3,606,930. As illustrated in FIGS. 1 to 3, the drill bit D
is threadedly connected to the lower portion 10a of the anvil so
that the bit can be replaced when necessary without necessitating
replacement or discarding of the anvil. As specifically shown, the
drill bit has an upper threaded box 100 formed with internal
straight threads 101, such threads extending downwardly from the
upper end 60 of the box, the box terminating in a bottom or lower
end wall 102 engaged by the lower end 103 of the anvil, the
impacting force imparted by the hammer piston 36 on the anvil being
directed from the lower end 103 of the anvil directly to the lower
portion of the bit. Thus, the bit D is threaded on the anvil until
the end wall 102 of the bit firmly engages the lower end 103 of the
anvil, the impact blows being transmitted directly from the anvil
to the bit, without any substantial portion of the impact load
being transmitted from the external threads 104 on the anvil that
mesh, through an intervening malleable sleeve 105, with the
internal threads 101 of the box. The reactive force of the anvil,
however, will be transmitted from the external threads 104 through
the malleable sleeve 105 to the box threads 101.
The internal threads 101, and also the external threads 104, are
generally V-shaped threads, the crests 106 of which have been
flattened and the root portions 109 of which are rounded. The
malleable sleeve 105, which may be of any suitable material, such
as copper or aluminum, may be press fit into either the box by
deforming the sleeve snugly into engagement with the thread
surfaces 108, 106, 109, or it may be pressed against the similar
thread surfaces of the external anvil threads 104. In any event, it
will be deformed so as to make a snug engagement with all surfaces
of the straight internal threads and all surfaces of the mating
external threads. If desired, the threaded sleeve 105 can be
preformed and inserted loosely into the box 100, the anvil 10 being
threaded into such sleeve, the tightening of the bit D on the anvil
producing the intimate contact between the sleeve 105 and the
internal and external thread surfaces described above. The sleeve
material, being ductile or malleable, will be deformed by the
threads where necessary to insure the uniform contact of the
ductile material with the external and internal threads 104, 101
and to insure even loading of the thread faces 108. Such
deformation will even occur under the repeated impact blows struck
by the hammer 36 upon the anvil 10 and transmitted through the
anvil to the bit D, as well as under the reactive forces resulting
from the rebound of the anvil after the blow is struck
thereagainst, and due to reflective waves that might travel through
the anvil.
It is to be noted that the male and female threads 104, 101 are
straight threads. The included angle x between the thread faces or
flanks 108 is preferably 90.degree., which adds greatly to the
thread strength. In addition, the straight threads are multiple
start, such as two-start, threads, which facilitates the threading
and unthreading of the bit onto and from the anvil. Any mismatching
between such multiple start or divided pitch of threads is
compensated for by the deformation of the malleable or ductile
intervening sleeve 105, since the material of the sleeve will be
displaced or flow wherever necessary as a result of the tight
makeup of the bit on the anvil, more uniformly distributing the
load over the thread surfaces.
The thickness of the ductile sleeve is suitably chosen. As an
example, it may vary from about 0.010 to 0.020 inches in thickness.
In lieu of employing a preformed sleeve, the malleable material,
such as copper, can be plated onto the box threads 101. In the
plating operation, the thickness of the sleeve 105 is somewhat
limited; for example, being of the order of about 0.008 inches in
thickness. Such relatively thin plating, although effective, may
not be as effective as the provision of a thicker sleeve of
material, since the copper plating will bond to the base material
therebeneath and may not yield or cushion properly to avoid high
localized stresses during the operation of the hammer
apparatus.
FIGS. 6 and 7 illustrate a method of deforming a sleeve 105 made of
a malleable or ductile material, such as copper or aluminum, into
the box threads 101 of the drill bit D. A straight cylindrical
sleeve 105a of an appropriate thickness, for example, 0.040 inches,
is inserted into the box 100, the outside diameter of this sleeve
closely conforming to the diameter of the thread crests 106 of the
box, the sleeve extending from the end wall 102 of the box to its
outer end 60. A mandrel 200 of steel, or other suitable material,
is then inserted into the box 100, this mandrel being encircled by
an initially retracted soft elastomer sleeve 201 fitting within the
copper sleeve or bushing 105a. A cylinder 202 bears against the
upper end 60 of the drill bit and has its lower internal diameter
203 closely conforming to the outside diameter of the elastomer
expander member 201. The inner wall 204 of the cylinder above its
lower portion is laterally spaced from the periphery 205 of the
mandrel to provide an annular space in which a hard rubber sleeve
206 is inserted that bears against the upper end of the soft rubber
sleeve 201. An annular piston 207 is received within the annular
space and bears against the upper end of the hard rubber sleeve
206.
The piston 207 is forced downwardly within the annular cylinder,
shifting the hard rubber sleeve 206 downwardly and causing the
latter to compress, shorten and deform the soft rubber sleeve 201,
which will expand the ductile sleeve 105a outwardly within the
internal spaces between threads 101 and bring it into snug
engagement with the thread flanks 108, as well as against the root
109 and crest 106 of the threads, the sleeve thereby being pressed
into intimate contact with the box threads 101 and assuming the
configuration illustrated in FIGS. 7, 1b, 2. The removal of the
endwise force on the piston 207 will cause the soft rubber sleeve
201 to inherently contract to its original shape, allowing the
mandrel 200, soft and hard rubber sleeves 201, 206, piston 207 and
cylinder 202 to be removed from association with the bit D.
The threaded connection embodying the intervening malleable sleeve
105 can be used at other locations in impacting devices, to insure
substantially uniform loading of the thread surfaces. As disclosed
in FIGS. 4 and 5, an impacting shaft 300 is provided between the
source of impact blow or blows and the drill bit D, the latter
being illustrated as being threadedly secured to the lower end of
an impacting shaft or rod section 301, there being an intervening
malleable or ductile sleeve 105 between the pin and box threads
104, 101. This shaft section has an upper externally straight
threaded section 302 threadedly received within a coupling 303,
which, in turn, is threaded onto the lower externally threaded
portion 304 of an upper impact or rod section 305, the lower end
306 of the upper section and the upper end 307 of the lower section
being in contact with one another so as to transmit the hammer or
impact blows therebetween. A ductile sleeve 105 is provided between
the external and internal threads of the upper pin 304 and coupling
sleeve 303, as well as between the lower pin 302 and coupling
sleeve 303, to insure the uniform transmission of load between the
external and internal thread surfaces, in the same manner as
described above in connection with the operation of the ductile
sleeve 105 between the external and internal anvil and bit threads
104, 101.
* * * * *