Threaded coupling for percussion drill bit

Abstract

An internally threaded bit for percussion drilling is provided, which has thread roots wider than the thread crests. A single drill bit, configured according to the present invention, can be connected to a variety of rods, having differing crest widths in their male threads. The invention enables the service life of the rods to be optimized to suit the drilling conditions at hand, without the need to manufacture and keep in inventory a correspondingly large variety of drill bits. The bit of the invention exhibits a reduced rate of ringing off, and can accept drill rods having a range of crest widths.

Claims

1. A drill bit for percussion drilling, having an internal female thread, wherein the thread is characterized by having: (a) a substantially trapezoidal profile, (b) a mean thread diameter in the range 28 to 35 mm, (c) a crest width a1 in the range 6.5% to 14.5% of the mean thread diameter, (d) a root width b1 in the range 23% to 30% of the mean thread diameter, (e) a ratio of root width to crest width in the range 1.5<(b1/a1)<4, (f) a flank angle α in the range 30 to 40 degrees, (g) a first curved profile, with a first radius from 1 mm to 5 mm, connecting the crest to the flanks, (h) a second curved profile, with a second radius from 0.5 mm to 4.5 mm, connecting the root to the flanks, and (i) the root having a flat portion of at least 4.0 mm length.

2. The drill bit according to claim 1, further characterized by having a pitch in the range 13 to 18 mm, and a thread depth in the range 1.2 to 1.8 mm.

3. The drill bit according to claim 1, further characterized by having a helix angle in the range 8.5 to 10 degrees.

4. The drill bit according to claim 2, further characterized by having a helix angle in the range 8.5 to 10 degrees.

5. The drill bit according to claim 3, wherein the helix angle is in the range 8.5 to 9.5 degrees.

6. The drill bit according to claim 4, wherein the helix angle is in the range 8.5 to 9.5 degrees.

7. The drill bit according to claim 3, wherein the helix angle is 9 degrees.

8. The drill bit according to claim 4, wherein the helix angle 9 degrees.

9. The drill bit according to claim 1, wherein the flank angle is in the range 34-36 degrees.

10. The drill bit according to claim 2, wherein the flank angle is in the range 34-36 degrees.

11. The drill bit according to claim 3, wherein the flank angle is in the range 34-36 degrees.

12. The drill bit according to claim 4, wherein the flank angle is in the range 34-36 degrees.

13. The drill bit according to claim 5, wherein the flank angle is in the range 34-36 degrees.

14. The drill bit according to claim 6, wherein the flank angle is in the range 34-36 degrees.

15. The drill bit according to claim 7, wherein the flank angle is in the range 34-36 degrees.

16. The drill bit according to claim 8, wherein the flank angle is in the range 34-36 degrees.

17. The drill bit according to claim 1, wherein the mean thread diameter is in the range 30 to 32 mm.

18. The drill bit according to claim 2, wherein the mean thread diameter is in the range 30 to 32 mm.

19. A method of percussion drilling comprising the sequential use of a drill bit according to claim 1 with a plurality of drill rods having different thread crest widths.

20. A method of reducing parts inventory at a percussion drilling site, comprising operating said site with said inventory containing a plurality of drill rods having different thread crest widths, wherein said inventory further contains at least one drill bit according to claim 1.

21. The drill bit according to claim 1, in combination with a drill rod having a male thread, wherein the male thread is characterized by having: (a) a third curved profile, connecting the crest of the male thread to the flanks of the male thread; and (b) a fourth curved profile, connecting the root of the male thread to the flanks of the male thread; wherein, when the rod is threaded into the bit, there is no contact between the curved portions of the rod thread and the curved portions of the bit thread.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 is a cutaway view of a typical prior art drill bit.

(2) FIG. 2 is a cutaway view of a drill bit of the invention.

(3) FIG. 3a shows a section of a drill bit of the invention, mated to a rod having a male thread with a crest wider than the root.

(4) FIG. 3b is a detail of the thread profile of the invention.

(5) FIG. 4a shows a prior art drill bit thread mated to a prior art drilling rod.

(6) FIG. 4b shows a drill bit thread according to the invention, mated to a rod having a male thread that fills the groove of the bit.

(7) FIG. 4c shows a drill bit thread according to the invention, mated to a rod having a male thread that partially occupies the groove of the bit.

(8) FIG. 4d shows a drill bit thread according to the invention, mated to rod having a matching crest width.

(9) FIG. 5a shows a bottom-drive embodiment of the invention.

(10) FIG. 5b shows a shoulder-drive embodiment of the invention.

DETAILED DESCRIPTION OF THE INVENTION

(11) The service life of a drill bit is normally determined by the wear of the carbide inserts, and can be very short in extremely abrasive grounds. As a result, the average life of a drill rod is much longer than the bit life, often ten times longer or more. This means that the bit threads are often in good condition when the bit itself has to be retired due to carbide wear or breakage. In other words, much of the thread wear volume in the prior art bits is never utilized. The present invention makes use of this wasted wear volume through a modified thread design, in which the unused wear volume is effectively transferred to the rod material. The working life of the bit threads can thereby be matched to the life of the bit itself, and the rods given a correspondingly longer working life.

(12) Manufacturers of drilling tools are confronted with the problem that their many different customers are operating under a wide range of different drilling conditions. For example, at some drilling sites the exposed rock surfaces at stope faces are badly weakened by previous blasts, and it is not easy to find a surface solid enough to effectively rattle loose a stuck bit. Excessive rattling causes damage to the tools, and a stuck bit puts the driller in danger when working outside the cabin, struggling to change the bit. A greater helix angle in the connecting thread is known to make the joint looser, thereby making it easier to change the bit, but this comes at the expense of an increased wear rate, a trade-off that may be worthwhile at one drilling site but not at another. For practical reasons, manufacturers have adopted a one-size-fits-all approach to the design of the drill bit to drill rod coupling, a compromise that often prevents the end user from making an optimal choice of bit and rod designs. The present invention provides the end-user with the ability to select the tools—in particular the drill rods—most suitable to the specific drilling conditions at hand.

(13) The present invention is directed to improving the threaded coupling between a drill bit and a single-pass rod in percussive tunnel drilling. FIG. 1 shows a typical prior art drill bit 1 having carbide cutting inserts 2. The bit features an interior female thread for accepting the male threads of a drill rod, with the rod and bit threads having common helix angle β. The expanded area of the drawing shows the length of a single thread pitch, where the thread comprises a crown or crest having width a, and a root or groove of width b, connected by flanks at a flank angle α. The most effective flank angle has been found, in practice, to be in the range of 30 to 40 degrees, with the industry having settled on 35 degrees as a standard. To the knowledge of the inventor, all bits in use today in the tunneling and mining industries have a˜b, which is true of the male threads on the drill rods as well, as shown for example in U.S. Pat. Nos. 8,066,307 and 7,185,721. This results in the total wear volume being evenly distributed between the bit thread and the mating rod thread, as shown in FIG. 4a, which is inefficient because the wear volume 5 of the bit is not consumed at the same rate as the wear volume 6 of the rod.

(14) Since most of the wear volume in the bit is wasted in conventional couplings, as explained above, allowing the root to have a greater width than the crest (i.e., b1>a1, as shown in FIG. 2) will not have a negative effect on the life of a bit 3 of the invention. However, the expansion of the root (and thus the groove) on the bit 3 makes it possible to increase the crest width a2 in the rod thread, as shown in FIG. 3a, dedicating more material to the wear volume of the rod thread than is possible in the prior art design. As a result, the rod can have a significantly longer service life than is achievable with the products now on the market.

(15) The ratio (b1/a1) according to the present invention is between 1.5 and 5, and preferably ranges from 2 to 4. The flank angle α is in the range of 30 to 40 degrees, preferably 34-36 degrees, and most preferably about 35 degrees. The helix angle β is related to the pitch and diameter of the thread by the formula
helix angle β=arctan[pitch/π(pitch diameter)]
where the pitch diameter is the mean of the major and minor diameters. As noted above, a greater helix angle makes it easier to loosen the bit by rattling. Preferable helix angles according to the present invention, suitable for single-pass drilling, range from 8 to 10 degrees, preferably from 8.5 to 9.5 degrees, compared to 6 to 8 degrees in most conventional threads. (The industry-standard R32 thread has a helix angle of 7.6°). Specific embodiments may have helix angles ranging from 9 to 9.5 degrees. These values are well outside of the combinations of pitch and flank angles disclosed in prior art publications such as U.S. Pat. Nos. 4,332,502 and 4,861,209.

(16) The pitch of the thread is preferably 13 to 18 mm, and the thread depth preferably ranges from 1.2 to 1.8 mm. In order to avoid jamming, clearance is provided between the major diameters of the rod and the bit threads (FIG. 3a), as well as between the two minor diameters. The radius R1, which connects the thread crest and its adjacent flanks, is larger than the radius R2 connecting the root bottom and its adjacent flanks, in both the bit threads and the rod threads, as shown in FIG. 3b. This feature serves to minimize contact and interference when the threads are engaged. R1 may range from about 1.0 to about 5.0 mm, and is preferably about 2.5 to 3.5 mm, while R2 may range from about 0.5 to about 4.5 mm, and is preferably about 2.0 to 3.0 mm. A straight section should preferably exist on the flank, the length of which is 20% to 75% of the flank length, preferably 33% to 50%. The term “substantially trapezoidal profile” refers to trapezoidal threads modified by incorporation of the above curvatures. This difference between R1 and R2 ensures that there is no contact between the curved portions of the rod and bit threads. This minimizes the risk of wear or damage near the roots of the threads, where it is more likely to lead to stress cracks and fractures.

(17) As further protection against rod failure, the rod thread may be given a greater height than the bit thread, so that the play between the root of the rod thread and the crest of the bit thread is greater than between the crest of the rod thread and the root of the bit thread.

(18) The ratio a2/b1 is the thread fullness, the degree to which the rod thread fills the groove of the bit thread, and this ratio is preferably in the range of 0.2 to 1.0. Depending on the specific drilling conditions, the end user can select rods with partial or full threads to obtain any degree of fullness in this range. If fatigue is not a concern, a high value of a2/b1, approaching 1.0, can be chosen, as shown in FIG. 4b, where the wear volume 8 of the rod is maximized, with the wear volume 7 of the bit only being sufficient to outlast the carbide inserts. In situations where fatigue failure is an issue, a smaller ratio can be chosen, as in FIG. 4c, so as to change the failure mode from fatigue cracking to the preferred mode of thread wear, by virtue of the reduced wear volume 9. In extreme cases, the wear volumes 7 and 10 can be matched, as in FIG. 4d, so that the rod and bit threads wear at approximately the same rate. FIGS. 4b-4d also roughly represent the progression of wear of a rod's threads, with the gap h increasing over time. It is a feature of the thread design of the invention that the bit and rod connection remains tight, even as the rod threads wear down and the gap h grows larger.

(19) U.S. Pat. No. 6,196,598 and US Patent Application Publications 2010/0001522 and 2010/0059285 discuss the use of a wider crest than root in the rod thread, so that a lower-cost sleeve coupling can be treated as a sacrificial part, in a manner similar to what is shown in FIG. 4b. However, due to the narrowness of the “notches” or thread grooves, the stress concentration at the thread root in these full-thread rods is greater than in the less-full rods. In many drilling sites such rods will fracture due to fatigue long before reaching the stage shown in FIG. 4c, let alone that shown in FIG. 4d. Therefore, the present invention gives the end user an option to start with a less full thread as shown in FIG. 4c so that fatigue fracture can be completely avoided. This provides an advantage over the use of conventional systems, when end users experience a sudden increase in rod breakage due to a change in drilling conditions. The usual response in the field is to blame this on a “bad batch” of rods. If conditions do not return to normal, the user will switch suppliers, which causes problems with logistics without actually solving the problem. A user of the present invention, in contrast, can simply switch to a less-full grade of rods, which are likely to be replaced due to wear before fatigue-related fracture sets in.

(20) Regardless of the fullness of the selected rod thread, all that are within the range will be compatible with the bits used for the full threads, as depicted in FIGS. 4b-4d. Hence, an end user can operate with a single bit thread design, without the issue of mismatch between the bit and the selection of rods kept on hand.

(21) A bit according to the present invention is also less likely to “ring off”. In ringing off, the bit fractures into two parts: most of the skirt separates from the head, which retains only a small portion of the skirt. This mode of failure is due to fatigue in the thread root closest to the bottom of the socket. The use of threads according to the invention does not negatively affect the wear life of the bit, as noted above, but the increased groove width reduces stress concentration at the thread roots, resulting in an increased service life and a reduced incidence of ringing off due to fatigue.

(22) The major and minor diameters of the thread on the bit may have a mean value ranging from 27 to 35 mm, preferably in the range of 30 to 32 mm. The crest width a1 in the drill bits of the invention ranges from 6.5% to 14.5% of the mean diameter, while the root width b1 ranges from 23% to 30% of the mean diameter. Thus, in the various embodiments, as the mean diameter is made larger, the pitch, and the values for a1, a2, b1 and b2, will be proportionally larger. Representative ranges of values for various mean diameters are shown in Table 1:

(23) TABLE-US-00001 TABLE 1 Mean diameter Crest width a1 Root width b1 (mm) (mm) (mm) 27 1.76-3.92 6.21-8.10 29 1.89-4.21 6.67-8.70 31 2.02-4.50 7.13-9.30 33 2.15-4.79 7.59-9.90 35 2.28-5.08 8.05-10.5

(24) By way of example, three embodiments of the present invention are described below in detail, with wear life increases for the rods calculated from their increased wear volume. From FIG. 4a it can be seen that the wear volume is roughly proportional to the crest length. Most of region wl is wasted wear volume that is never utilized in the prior art bits. The standard R32 (ISO 10208) thread is a rope thread, where the crown is continuously curved, therefore the wear volume is slightly less than in the illustrated trapezoidal thread, where the crests are flat. A trapezoidal thread with the 12.7 mm pitch of the R32 thread will have a crest length of 4.2 mm, which number is used in the following examples to calculate the wear life increases. These increases would be even larger relative to the wear of a rod having an R32 rope thread, which starts out with a smaller wear volume.

EXAMPLE 1

(25) Major diameter=32 mm Minor diameter=29 mm Thread depth=1.5 mm Pitch=15 mm Helix angle=8.9° Flank angle α=35° a2=b1=7.7 mm b2=a1=3.0 mm Thread fullness a2/b1=1.0 The rod wear life increase, from that of R32, is at least 83%.

(26) In this embodiment, the crest width a1 is reduced from 4.2 mm to 3.0 mm in the bit, and the crest a2 of the rod thread fully occupies the valley in the bit thread (FIGS. 3a and 4b). If an even larger increase in the wear life is desired, a1 could be further reduced to 2.0 mm to accommodate an even larger a2. To have sufficient thread strength, however, a1 is preferably not less than 2.0 mm.

EXAMPLE 2

(27) Major diameter=32 mm Minor diameter=29 mm Thread depth=1.5 mm Pitch=14 mm Helix angle=8.3° Flank angle α=35° a2=5.5 mm b1=7.2 mm a1=2.5 mm b2=4.2 mm Thread fullness a2/b1=0.76 The rod wear life increase, from that of R32, is at least 31%.

(28) In this embodiment, illustrated in FIG. 4c, the crest width a1 is reduced from 4.2 mm to 2.5 mm in the bit, and the crest of the rod thread occupies the valley in the bit thread with a fullness of 0.76, leaving a gap h of 1.7 mm. A partially-full thread on the rod, as in this embodiment, is easier to break loose from the bit, and also results in a reduced stress concentration at the root corners of the rod threads, where fatigue cracks are known to arise.

EXAMPLE 3

(29) Major diameter=33 mm Minor diameter=30 mm Thread depth=1.5 mm Pitch=16 mm Helix angle=9.2° Flank angle=35° a2=7.0 mm b1=9.2 mm b2=4.7 mm a1=2.5 mm Thread fullness a2/b1=0.76 The rod wear life increase, from that of R32, is at least 67%.

(30) In this embodiment, also represented by FIG. 4c, the diameter and pitch of the threads has been increased. The crest width a1 is again 2.5 mm in the bit, and the crest of the rod thread does not fully occupy the groove in the bit thread, leaving a gap h of 2.2 mm. This design, like example 2, serves the situations where the fatigue failure of the rod is a concern. This embodiment demonstrates that even without a full thread, a significant increase in the rod wear life can be achieved.

(31) The invention, broadly, provides drill bits having thread roots wider than the thread crests. The invention further provides a method of accommodating multiple drill rod thread profiles with a single bit. Accordingly, the invention further provides a method of operating a drilling rig with a variety of drill rod profiles, without the expense of a corresponding variety of drill bits, and a method of reducing the inventory of drill bits at a drilling site.

(32) The principles of this invention have been illustrated with trapezoidal threads in the drawings and examples, but the invention is contemplated to be operable with embodiments having continuously curved threads, and threads of intermediate form.

(33) The drill bits of the present invention can be employed either in so-called bottom-drive mode where the rod end impacts the bottom of the bit socket, or shoulder-drive mode where there is a gap between the rod end and the socket bottom, as depicted in FIGS. 5a and 5b, respectively. The latter mode provides a more rigid assembly, a quality much desired by drillers, especially during collaring (the initial formation of the drill hole.)

(34) The above detailed description, and the attached drawings, present specific and non-limiting embodiments and examples of the invention. Modifications, equivalents, and variations that are obvious to those of skill in the art are contemplated by the inventor to be part of this invention, and the following claims are intended to be construed accordingly.