EP3143237A2 - Joint and joint parts for drill string components - Google Patents

Abstract

A joint for joining together drill string components (6, 7) of a drill string for percussion drilling, the joint including a male part (8) and a female part (9) f wherein a first impact surface (10) is arranged to co-operate with a second impact surface (11). When the drill string is in operation, relative axial movement is allowed, between the male (8) and the female (9) parts when the first and the second impact surfaces (10,11) are adjacent to each other. The invention also concerns a male joint part, a female joint part, a drill rod, a shank adapter, a drill head, a drill bit and a drill string component.

Description

JOINT AND JOINT PARTS FOR DRILL STRING COMPONENTS AND

COMPONENTS

FIELD OF THE INVENTION

The invention relates to a join for a drill rod. The invention also relates to parts of such a joint and a drill rod and other drill string components including such parts.

BACKGROUND OF THE INVENTION

Drill strings for percussion drilling are typically composed of a number of drill string components, such as drill rods, that are connected to each other via a threaded joint. The function of the drill rods is to transmit rotation, feed force and percussive impacts from the percussive rock drilling machine to the drill bit. Flushing medium is also transmitted through the drill rods.

When, the bore hole is completed or in case the drill bit has to be replaced prematurely, the drill string has to be retrieved by pulling it out of the bore hole and be

successively disassembled.

Today's conventional drill rods are simple to use and associated with low tooling costs. There are, however, drawbacks associated with the use of today's drill rods such as hole deviation and zig-zag-shaped hole walls. The

requirement for skilled and experienced operators in order to obtain acceptable quality results is also a problem.

The threaded joints limit the working life of the rods since the threads are frequently subjected to wear and

different kinds of failures such as breakages. Furthermore, in order to ensure secure drilling, the threaded joints have to be continuously tightened so as to ensure proper shock wave transmission all the way through the drill string. In order to loosen threads prio to disassembly, the drill string has to be frequently rattled.

When it comes to operator skills, an experienced driller is required in order to most o timally tune feed force and rotation and foe careful and observant during start of drilling and to adapt, drilling parameters to rock properties,

encountered rock formations, start angles vis-a-vis drilling direction etc

The thread joints are subject to wear and are exposed to risk of failure for many reasons. Meeting threads are subject to relatively sliding or rubbing wear long udinally due to percussion waves and reflections as well as laterally because of torsional shock waves generated when the bit cuts into the rock to the extent that thereby rotation is drastically slowed momentarily.

In the root of the last turn of the male thread, the stress concentration facto can be greater tha three, thus setting an upper limit to the allowed percussive stress level.

The virtually universal non-linearity of bore holes produced with conventional drill i-ods in the drill string results in pulsating bending moments affecting the threaded joints. A threaded joint has potential for high stress

concentration resulting from such bending moments. Added to bending moment resulting from hole-dev at on and. human error, prematur fatal failures occur frequently.

Finally, so-called "drilling loose" and also extensive rattling to loosen joints upon completion at a hole will induce excess damage to the joint. If not performed correctly, severe damage or even breakage can occur.

In respect of a drill rod system intending to reduce problems with conventional drill string components there has been suggested to have the percussive shock waves by-passing the threads via a separat stack of rods provided in the centre of a series of tubes which a e- interconnected with threads. This system delivers high top-hammer penetration rates with quality corresponding to a down-the -hole drilling system and long service life. Because of relatively high investment costs, this system has so far reached only a high end market.

EP0387218 describes a background art drill string component, having a central rod surrounded by a tube.

WQ03097881 Al, US6293360 and US468736S describe threaded drill string components. WO2008/004937 Al describes a non- hreaded joint for drill string component

AIM AND MOST IMPORTANT FEATURES OF THE INVENTION

It is an aim of the present invention to provide a system that solves or at least reduces the problems mentioned above.

This aim is obtained ih a joint for joining together drill strin components for percussion drilling, wherein each drill string component extends along an axial direction, and Wherein, in operation, impact shock waves and rotation torque are arranged to be transferred via the joint, the joint including a male part and a female par having meeting impact surfaces. The invention is d stingu shed in - that the male part exhibits: i, first rotation torque transfer means, and ii . first axial coupling means, - that the female part

exhibits; iii. second rotation torque transfer means, and iv. second axial coupling means, - wherein the first and second rotation torque transfer means extend on the respective male and female parts such, and - wherein the first and second axial coupling means are positioned such - that when the drill string is subjected to rotatio torque for drilling, relative axial movement is allowed betwee the male and the female parts when being in an interconnected state of co-operation between, the first and second rotatio torque transfe means. which is when the first and the second impact stirfaces are adjacent to each other.

Hereby several advantages over the background art are achieved. The invention wak s it possible to transmit both rotation and percussive shock waves through the drill string over only two meeting elemen s in the joint. This is achieved ith a hole quality being comparable to system as described above (Copro ©) , wherein transmission of rotation and of percussive shock waves is separated in two separate elements for each drill string component unit .

A drill string component including one or two parts of a joint according to the invention is hereby comparatively easy and cost-effective to produce and with a weight being about half tha of a corresponding Coprod - element. In order to separate the individual components, there will no longer be required to rattle the drill string and since a joint can be produced such that bending forces are greatly reduced, the expected working life of the components goes far beyond that of conventional one piece drill rods.

In order to drill high quality holes there is less demand on skilled and experienced drillers, and altogether it has been made possible to drill hole of high quality at a low cost .

According to the invention, the first and the second rotation torque transfer means are laid out such as to allow a relative axial movemen between the male: and the female parts in the interconnected state in a region close to where the first and the second impact surfaces contact each other. In particular, a minor relative displacement between the male and female parts is allowed stabsequent to an impact shock wave passag ,

The magnitude o the relative axial movemen or

separation between the parts of the joint is normally expected to be from about 0,2 to about 0,6 mm during drilling. The separation between the parts of the joint can, however in case of drilling in very hard rock and. with a drill hammer without damping even be expected to be as high as between about 1,2 - .1,6 mm. Prilling in rock with cavities could result i even greate separation than that.

For that reason the joint is preferably constructed £or allowing at least 1 mm separat on and preferably 2 mm or more of separation. It should, however be understood that the inventive joint can be constructed for considerably higher degree of separation such as even up to about 100 mm.

Hereby it is avoided that high forces that otherwise would affect the components subsequent to a percussive shock wave passing the joint have to be received by elements of threads belonging to the joint parts.

instead thes forces are counteracted by the feed force provided through the dri l string. This is a great advantage, Since it is no longer necessary to dimensio joint parts, such as thread ridges, for receiving and counteracting these forces. Therefore a significantly longer service life is possible for an inventive joint. It is also possible to produce the inventive joints for allowing certain mutual misalignment between adjacent string components without inducing particular bending moments corresponding to what is being so harmful for conventional threaded joints.

Another advantage is that the inventive joint provides greater energy transmission efficiency than, that of

conventional threaded connections.

It is important to understand that, during percussion drilling, the drill hammer subjects th drill string to intens repeated impacts in the order of 200 MPa, whereby shock waves are transmitted from drill string component to drill string component, passing via the joints of the drill string all the way to the drill bit. This initial shock wave is in the form of a compressional wave propagating through the material of the drill string.

As a result of reflexion at the bit end of the drill string of the initial shook wave, either a tensile wave or a compressional wave is generated propagating back through the drill string. Passage via joint of these reflected waves has a separating effect to impact surfaces of the joints.

In a threaded joint, separation is counteracted by the thread ridges resulting in subsequent fatigue problems and wear. Such a threaded joint is pre-loaded. In the case of bottom-drive the female part is in tension and the male part is in compression. In the case of shoulder-drive the situation is the ppposite. When an impact wave arrives,, th pre-loaded joint undergoes a partial or even a full release. Upon the passing of the shock wave, the joint regains its full preload.

The drill string is also subjected to repeated reflected shock waves, either tensile or compressional . These reflected shock waves will either increase or decrease the degree of the pre-loading, adding more releasing and reloading effec to the joint. The elastic deformation associated with all these releasing and reloading effects causes relative movements of the two parts being connected, but there should be no rigid- body separation between them at any time. I.e. the impact surface of the male part is in constant contact with the impact surface of the female part.

A feed force applied to the drill string depends on various parameters but can be said to be in the region up to about 5 MPa, i.e. only a minute fraction of the shock wave value _*

No realist c feed force can. in any joint construction prevent shock wave passage induced influence to the joint parts. According to the invention, the problem associated with such influence is solved through the inventive completely new approach in allowing a certain relative axial movement between the parts, Hereby the intense but very short-las ing forces induced by the shock wave passage can foe effectively absorbed by being counteracted by the f ed force over a relatively longer period during the relative axial movement between the parts.

In order to ensure that a relative axial movement between the parts can be obtained in prac ce during drilling, the inventive joint per se is free from pretension in eithe rotational or axial direction when being subjected to rotation for drilling. Any such pretension would result in mutually locking parts, wear because of relative micro-movements and fatigue problems.

It is therefore important, that co-opera ing., meeting, surfaces of th first and second rotation torque transfer means ar arranged to contact each other in a rotational direction such tha self-locking and pretensioning of the joint can not occur. This is achieved in that an angle between a flank direction, and a radius where th contact occurs betwee two meeting surfaces of the first and second rotation torque transfer means is great enough to avoid self-locking and pretensioning of the joint. The angle is preferably at least 45°, more preferred over 60° and most preferred over 70^!\ Hereby no tendencies of self-locking occurs.

An important purpose of the first and the second axial coupling means of the male and the female parts is basically to ensure safe retrieval of the drill string. It is important to understand that in the interconnected state of two adjacent drill string components, the first and the second axial coupling means do not obstruct the relative axial movement between the joint parts. For that reason, at least in a state where the drill string is subjected to rotation torque or drilling, the first and the second axial coupling means allow and do n obstruct said relative axial movement.

With "joint for joining together drill string

components" , her ie in particula intended joints between tubular components that are to be positioned between a percussive rock drilling machine and drill bit for

percussion drilling since the invention is particularly advantageous for such components often referred to as a drill rod. This definition also includes a joint between the shank adapter and the first drill rod.

The first and second rotation torque transfer means are preferably mating splines that are preferably comprised, fox- each one of the male and the female parts, of at least six ridges that are elongated and that extend along each one of the male and the female parts. Ridges are protruding radially inward© from an inside wall of a cylindrical member to form female splines_* Ridges are protruding radially outwards from an outside wall of a cylindrical membe to form male splines.

It is in principle undesirable to have rotation inducing considerable contractive effect in the joint, because of the above mentioned force reception as well as the creation of. undesired rigidity in the joint resulting in risk of fatal failure problems. Contacting surfaces therefore preferably extend in parallel with said axial direction o the respective male and female parts.

It is, however, in some instances advantageous to have the contacting surfaces extending slightly helically in th direction of contraction on. the respective male and female parts of the joint when the drill strin ie sub ected to the normal forward rotation during drilling. This contraction must, however, be limited and contacting surfaces must extend so as not to prevent relative movements between the male and the female join parts which could result in tendencies of the above problems. For that reason the helix angle of the

contacting surfaces should preferably normally be from -20" up to abou 20° to the axial direction. Negative values means that separation of the impact surfaces because of the above described effect results in. separation between meeting first and second rotation torque transfer means.

Forming th rotation torque transfer means helically is more complicated and expensive compared to forming these surfaces axially extending, but gives a somewhat softer rotation torque transfer between adjacent components.

Th joint is obviously not preloaded as a conventional threaded joint for drill string components.

In case the contacting surfaces extend axially, basically no force inducted by the joint itself restricts the relative axial movement, between the joint parts.

The first and second 1 coupling means

advantageously include axial engagement means formed by radially directed protrusions on one of the male and the female parts,

Axial engagement means, advantageously includes radially directed protrusions in the form of hook elements or abutments on one of the male and the female parts for

engagement with, abutment surface portions on the other one of the mal and the female parts. The axial engagement means are intended for temporary axial locking so as to limit and prevent exaggerated, separatio between the joint parts. One example when this is required is for allowing quick lifting of the drill string for clearing the bore hole from stuck drill cuttings.

The axial engagement means can be arranged such that the rst and th second axial coupling means, in an

interconnected state of the joint, are made to engage in a positive, forward, rotation direction, i.e. in the normal rotation direction used during rock drilling or in the opposite, reverse, direction, whereby the connection is locked during reverse rotation but not locked during drilling. In the latter case, it will not be required to have an auto rod changer on the rig. It is also possible to have a joint arranged for locking in both forward rotation direction and in the opposite, reverse, direction. This embodiment is

particularly advan ageous for use for a shank adapter whereby faster operation is achieved. In all locking, axial movements between the parts is limited according to the above.

It is preferred that one of the first and second axial coupling means, is constituted by end surfaces of splines on the male or female part for co-operation with the above mentioned hook elements or abutments. No extra elements have to be provided with this embodiment.

It is preferred that the first and second axial coupling means include axial security coupling mean . Thi provides for safe prevention against any accidental release of the joined components. Mos preferred the axial security coupling means includes a thread coupling or a bayonet coupling.

Advantageously, second axial security coupling means in the form of outside threads are positioned at a distal portion of a sleeve-shaped or rod-shaped element extending centrally of the female part and that mating first axial security coupling means in the form of inside threads are positioned at a distal portion of the male part. Suitably a dista portion of the rod-shaped element is cup-shaped with holes for lushing fluid and a rod base has holes for flushing fluid in order to ensure advantageous fluid transfer through the drill string durin operation.

It should be noted that it is advantageous to provide the one and the same inventive join with first and second axial coupling means including axial security coupling wea s as well as axial engagement means for both safe drill string retrieval a d enhanced functionality according to the above.

The first and second axial coupling weans can be arranged in various ways and for example, ass threaded means engaging only during a first stage of connection of two adjacent components. Hereby, upon termination 6f that first stage, free movement along the mating first and second rotation torque transfer means is allowed all the way to the operational position where the impact surfaces of the two adjacent

components meet. In order to avoid that meeting end surfaces of splines initially abut each other axially and obstruct the connection phase, the end surfaces can be made pointed.

Alterna vely, bayonet coupling means can be used or intermeshing hooks on the inside of one of the first and second rotation torque transfer means that engage with inside ends of the second of the first and the second rotation torque t ansfer means or hooks or lugs on an outside of one of th first rotation torqu transfer means for engagement with the outside of th other one of the first and second rotation torque transfer means. Said hooks or lugs make up the first and a second axial coupling means.

In a preferred variant, the female part includes an inner and an outer, dual-wall construction, the walls being sleeve-shaped together to define an annular compartment for the reception of a sleeve-formed (portio of a) male part.

The first rotation torque transfer means can be positioned on one f the inside and the outside of the sleeve- formed male part, whereas the first axial coupling means can be positioned on one the same side or on the opposite side from the first rotation torque transfer means.

It is preferred that a sealing arrangement is positioned at an iriside opening slot formed between the male and the female parts., as seen in an operative position with the first and second impact surfaces close to each other.

The irst and second impact surfaces can be arranged for either shoulder drive, bottom drive or dual drive (both shoulder and bottom drive) ,

For clarifying purposes; In shoulder drive, impact surface shoulders are ring-shaped and are positioned radially outside th first and second rotation torque transfe means and the first and second axial coupling means.

Shoulder drive has proved to be most advantageous for use with respect to the invention, since shoulder drive joints tend to be less subjected to wear because the transfer of the shock wave outside and i parallel with the portions of the joint parts supporting the rotation transfer means. Another important advantage With shoulder drive is that it m kes it. more easy to provide for a virtually closed continuous outside surface for th entire drill string. In particular it is possible to make the entire drill string or at least the regions of the joints between th individual drill string components forming a continuous cylindrical envelope surface. This reduces ware.

It is also important that during the small relative axial movements in the joint in operation, impurities are prevented to enter into the joint. The risk for tha is minimized by using shoulder drive and having mating co~ operating circular cylindrical guiding surfaces closest to the meeting impact surfaces of two joining drill string

components. Flushing fluid leaking between th impact surfaces when they are slightly separated adds to reduction of the risk for impurities entering the joint.

It is advantageous in a more easily produced variant; that the female part is sleev -shaped with one wall, having both the second rotation, torque transfer means and the second axial coupling means being oriented on an inside sleeve wall.

Advantageously an angle between a radius of. the joint parts and a flank direction forming a right angle against a main surface of. the rotation torque transfer means is 60° - 90° and mors preferably 70^ - 90^¾. Hereby unwanted self-locking of the parts in a rotational direction is avoided and wear during drilling reduced to a minimum.

It is highly advantageous that the male part externally has a proximal, cylindrical guide portion for co-operation, with an internal, cylindrical guide surface at a distal portion of the female part. Advantageously, the male part at a distal region has part cylindrical outsid guide surfaces for co-operation with an. internal, cylindrical guide surface at a proximal portion of the female part. Hereby advantageous alignment of the joint is achieved.

The invention also relates to a male part of a joint for joining together tubular drill string components to be

positioned between a percussive rock drilling machine and a drill bit of a drill string fo percussion drilling, wherein each drill string component extends along an axial direction, and. wherein, in operation, impact shock waves and rotation torque are arranged to be transferred via the joint, wherein the male part is part of a first drill string component and is arranged to co-operate with a female part of a second drill string component, and wherein a first impact surface on the male part is arranged to co-operate with a second impact surface on the female part. The inventive male part exhibits t i. first rotation torque transfer means, and ii» first axial coupling means, for co-operation with iii. second rotation torque transfer means, and iv. second axial coupling means o the female part, - wherein the first rotatio torque transfer means for contacting the second rotation torque transfer means extend on the male part such, and ··· wherein the first axial coupling means for co-operation with the second axial coupling means is positioned such - that when the drill string is subjected to rotation torque for drilling, relative axial movement is allowed between the male and the female parts when feeing in an interconnected state of co-operation between the first and second rotation torque transfer means, being when the first and the second impact surfaces are adjacent to each othe .

Preferably, the first rotation torque transfer means ars splines having contacting surfaces that extend in parallel with said axial direction on the male par or extend helically on the respective male parts, at a helix angle (a) between 0° and 20° to the axial direction.

Suitably, the first axial coupling means include axial engagement means formed by radially directed protrusions on the male par ,

Preferably, the axial engagement m a s includes radially directed protrusions in the form of hook elements or abutments on the male part for engagement with abutment surface portions on the female part.

When the male and the female parts are

interconnected, the axial engagement means are arranged to engage in forward rotation of the drill string and/or reverse rotation of the drill string and thereb limit relative axial movement between the male and the female part.

Preferably, the first axial coupling means, is constituted by end surfaces of splines on the male part.

Preferably, the first axial coupling means include axial security coupling means. Hereby the axial security coupling means preferably includes a thread coupling o a bayonet coupling. When second axial security coupling means! in the form of outside threads are positioned at a distal portion, of a sleeve- haped or rod-shaped element extending centrally of the female part, mating first axial security coupling means in the form of inside threads are advantageously positioned at a distal portion of the male part.

The f rst rota ion torque transfer means is preferably positioned on one of the inside and the outside of the sleeve-formed male part.

The first axial coupling means is preferably positioned on one of the inside and the outside of the sleeve- formed male part.

A sealing arrangement is preferably positioned at an inside opening slot formed between the male and the female parts, as seen in an operative position with the first and second impact surfaces close to each othe .

The first impact surface is preferably arranged fo one from the group: shoulder drive, bottom drive and dual drive .

When the first impact surface is arranged for shoulder drive_/ outside surfaces, of meeting drill string components, at least in the region of the joint, form an essentially continuous envelope surface.

An angle (β) between a radius ( ) of the joint parts and a flank direction {f) forming a right angle against a main surface of the rotation torque transfer means is preferably 60^£

- 90° and more preferably 70° - 90°.

The male part has preferably externally a proximal, cylindrical guide portion for co-operation with an internal, cylindrical guide surface at a distal portion of the female part..

Th male part has preferabl at a distal region part

cylindrical outside guide surfaces for co-operation with an interna.!. , cylindrical guide surface at a proximal portion of the female part.

The invention also relates to a female part of a joint for joining together drill string components of a drill string for percussion drilling, wherein each drill string component extends along an axial direction, and wherein, in operation, impact shock waves and rotation torque from a percussion drilling machine at one end o th drill string is arranged to be transferred via the joint to a drill bit t an opposite end of the drill string, wherein the female part is part of a second drill string component and is arranged to co-operate with a male part of a first drill string component, wherein a second impact surface o the female part is arranged to cooperate with a first impact surface on the male part. The inventive female part exhibits: i. second rotation torque transfer m an©, an ii. second axial coupling means fo cooperation with iii. firs rotatio torque transfer means, and iv. first axial coupling means, on the male part, - wherein the second rotation torque transfer means for contacting the f rst rotation torque transfe means extend on the female par such, and - wherei the second axial coupling means for cooperation with the first axial coupling means is positioned such ~ that when the drill string is subjected to rotation torque for drilling, relative axial movement is allowed between the male and the female parts when being in an

interconnected state of co-operation between the first and second rotation torque transfer means, which is when the first and the second impact surfaces are adjacent to each other.

Preferably, the second rotation torque transfer means is splines having contacting surfaces that extend in parallel with said axial direction on the female part or extend

helically on the female part, at a helix angle Co) between 0° and 20° to the axial direction. The second axial coupling means preferably include axial engagement means formed by radially directed protrusions on one of the female parts.

The axial engagement means preferably includes radially directed protrusions in the form of hook elements or abutments on the female part for engagement with abutment surface portions one the male part.

When the male and the female parts are

interconnected, the axial engagement means are arranged to engage in forward rotation of the drill string and/or reverse rotatio of the drill string and thereby limit relative axial movement between the male and the female part ,

Preferabl the second axial coupling means is constituted by end sur ces of splines on female part .

Preferably the second axial coupling means include axial security coupling means.

Preferably the axial security coupling means includes a thread coupling or a bayonet coupling.

Second axial security coupling means in the form of outside threads are positioned at a distal portion of a sleeve-shaped or rod-shaped elemen extending centrally of the female part for matin with first axial security coupling means in the form of inside threads that are positioned at a distal portion of the male part.

The female part preferably includes an inner and an outer wall, together defining an annular compartment for the reception of a sleeve-formed male part.

A sealing arrangement is preferably positioned at an inside opening slot formed between the male and the female parts, as seen in an operative position with the first and second impact surfaces close to each other.

The second impact surface is arranged for one from th group; shoulder drive, bottom drive and dual drive. When the second impact surface is arranged for shoulder drive, outside surfaces of meeting drill string components, at least in the regio of the join , preferably form an essentially continuous envelope surface.

The female part is preferably sleeve-shaped having both the second rotation torque transfer means and the second axial coupling means being oriented on an inside sleeve wall.

Advantageously, an angle { } between a radius (R) of the joint parts and a flank direction if) forming a right angle against a main surface of the rotation torque transfer means is 60* - 90° and more preferably 70° - 90°.

When the male part externally has a proximal , cylindrical guide portion, it preferably co-operates with an internal, cylindrical guide surface at a distal portion of the female part.

It is preferred that when the male part at a distal region has part cylindrical outside guide surfaces, it cooperates with an internal, cylindrical guide surface at a proximal portion of the female part,

Shoulder drive is preferred because the shock wave can be transferred past the joint outside the very coupling elements making up the rotation torque transfe means and the axial coupling means. Hereby wear is reduced compared to what is the case with respect to a bottom drive, solution, see also the above for more advantages of shoulder drive.

The advantages explained above that are relating to the inventive joint are correspondingly achieved in respect of the male and the female parts. Subordinate optional features relating to th inventive joint are applicable also in respect of the inventive male and female parts.

Ail inventive dril rod includes one such male part or/and one such female part or two such male parts or two such female parts . An invent;ive shank adapter for a rock drilling machine includes one such male part or one such female part.

There are numerous ways in producing drill string components according to the invention. One method frequently used for producing drill rods is to friction weld the male and female parts onto a pipe-shaped rod blank. When it comes to femal parts having the dual-wall construction, an inner sleeve making up the inner wall or an outer sl ve making up the outer wall may be friction welded to a base part including the other one of the walls.

The drill rod according to the invention is also

advantageous for use in drill strings for down the hole hammers that produce impacts at the end of a drill string as well as for drill strings for rotational drilling (e.g.

tricone} only.

The inven ion also relates to a method for joining together tubular drill string components to be positioned between a percussive rock drilling machine and a drill bit for percussion drilling, wherein each drill string component extends along an axial direction, and wherein impact shock waves and rotation torque are transferred via a joint, including the steps of i- initiating axial insertion of a mal part of a first drill string component into a female part of a second drill string component,- rotate the first drill string component relative to the second drill string component to ensure engagement of axial security coupling means in the farm of a thread coupling or a bayonet coupling, - continue axial insertion of the male part into the female part a determined distance whereby the first drill string component is allowed to rotate relative to the second drill string component to ensure engagement of axial engagement means and to ensure engagement of first and second rotation torque transfer means arranged on the respectiv male and female part . Further details and advantages are explained in the below detailed description of embodimen s.

B IEF DESCRIPTION OF DRAWINGS

The invention will now be described in greater detail at the background of embodiments and with reference to the annexed drawings , wherein :

Fig. 1 shows, in a simplified side view, partl in section, a top hammer with a drill string including drill rods and drill bit,

Figs. 2a, b and a show in axial views a first embodiment of a joint with joint parts of a first and a second drill rod in three different states of connection,

Fig. 2cl shows a cross section of the first embodiment and Fig. 2c2 shows in a greater scale a contact region between two meetin splines.

Figs. 3 - d show in different views a second embodimen of a joint according to the invention,

Fig, shows a. different joint part,

Figs. 5a: - d show a details of different joint part in different positions,

Fig. 6 illustrate an alternatively constructed joint,

Figs. 7a and b show further different joint parts,

Figs. 8a - e show a further different joint and joint parts,

Figs. 9a and b show an alternative male joint part, Figs. 10 and b show a further alternative male joint par ,

Fig. 11 shows a shank adapter in a side view.

DESCRIPTION OF EMBODIMENTS

Similar and like elements are indicated wit same reference numerals in different figures. The top hammer l in Fig. 1 is movably supported by a (not shown} feed beam of a drill rig and is arranged to deliver impacts and a rotational movement to drill bit 3 in order to disintegrate rock .

A shank adapter 5, partly inside a front end region of the top hammer 1, connects to a drill string component being a drill rod of the drill string 2, said drill strin being composed of a number of drill string components such as individual drill x^*ods 4 that are connected via joints,

The drill bit 3 is connected to the lowermost drill rod 4 of the drill string 2 via a drill head 31.

An example of an inventive joint for joining together drill rods according to the invention is shown in Figs 2a, 2b and 2c. A first drill rod 6 has a male part 8 to be connected to a female part 9 of a second drill rod 7, The male part 8 is in this embodiment formed tubula as a sleeve having a free, distal, end and a proximal end being fastened to a tubular main part of the first drill rod 6.

The dr ll rods have an ajcially extending flushing channel for allowing a flow of flushing fluid from the top hammer to the drill bit.

The joint in Fig. 2a - c is constructed for shoulder drive and 10 indicates a first impact surface at a shoulder being included at a proximal end of the male part and being directed axially for co-operation with a second impact surface 11 at a most distal end of the second drill rod 7. In this case there is provided shoulder drive impact between the drill rods 6 and 7 such that the impact waves pass radially outside the elements securing connection of the drill rods to each other.

I is also possible to have bottom drive, in which case an alternative impact surface at the distal end of the male part would have been arranged for co-operation with an alternative impact surface on (a bottom portion of) the fem le part. In so called "dual drive", shoulder drive as well as bottom drive would be active.

The male part 8 exhibits firs rotation torque transfer weans being in the form of splines 12 in to this embodiment , The spl nes 12 extend axially in parallel with an axis A of the drill rods 6 and 7, and are arranged evenly distributed on an outsid surface of th sleev -formed male part.

In an interconnected state of the male and female parts, the first rotation torque transfer means 12 co-operate with mating second rotation torque transfer means 14 being arranged on an inside surface of a portion of the female part 9.

The male part 8 further includes first axial coupling means 13 in the form of a short scre thread on an inside surface of A d at a distal region of the sleeve -formed male part 8. The rst axial coupling mean 13 is arranged to cooperate with mating second axial coupling means 15, also in. the form of a short screw thread on a portion of the female part 9 being positioned radially inside the second rotation torque transfer means 1 and directed radially outward_*

The female part 9 in thi embodiment includes two sleeve- shaped coaxial members together forming an annular space or compartment for more or less completely receiving the coupling elements of the male part 8. Hereby the f male part ha an inner and an outer, dual-wall construction, to define said annular compartment for the reception of the sleeve-formed {portion of the) male part. In the shown embodiment according to Pigs. 2a ^«. 2c, the second axial coupling means being a short male screw tread is arranged at a distal region of an inner one of the sleeve-shaped coaxial members that together forming an annula space or compartment for receiving the coupling elements of the male part 8. In Fig. 2a, the male part 8 and the female part 9 are shown in. a state where, the male part 8 has been inserted into the annular space of the fe le part 9 and the first axial coupling means 13 engage the second axial coupling means? 15 by the short screw threads being threaded together with each othe .

In the state shown in Fig. 2 , the male part 8 has bee threaded further with respect to th female part 9 in that the short screw threads being the first and second axial coupling means 13 and IS have been through-threaded, passed their relatively short axial lengths. The ifiale part 8 can now basically be free to move axially into said annular space or compartment being formed in the female part 9, whereupon the splines being the first and second rotation torque transfer means 12 and 14, can come into engagement with each other so as to transfer rotation, torque between the first and the second drill rods.

stat where th first and second rotation torque transfer means 12 and 14 have come into engagement with each other is illustrated in an axial and a radial sections in Pig. 2c, wherein the couplin elements of the male part 8 has been completely pushed into said annular space inside the female part 9 such that the first and second impact surfaces 10 and 11 contact each other.

The position shown in Fig. 2c is the operative position, wherein, during drilling, impact shock waves can be

transmitted over the joint from the irst drill rod 6 to the second drill rod 7 over the meeting impact surfaces 10 and 11.

Since the rotation torque transfe means 12 and 14 are also in engagement in this position, rotation induced by the top hammer can also be transferred from the first drill rod 6 to the second drill rod. 7. According to the invention it is provided that tendencies! to separate the impact surfaces 10 and II occurring

immediately upon impact and also upon possible shock wave reflections passing the joint are not counteracted by the elements making up the joint. On the. contrary, a relative movement of the male part 8 and the female part 3 is possible which is counteracted neither by the co-operating rotation torque transfer means nor by the axial coupling means.

It is also ensured, according to the invention, that relative bending of the first and second drill rods does not essentially affect the wale and the female parts of the joint, since also a limited relative bending movement is allowed.

Altogether, the joint parts are not at all affected by harmful forces to the extent that normally affect joint parts of background art threaded joints.

Fig. 2a illustrates a drill rod 6 being produced by a tubular member being friction welded together with an element essentially making up the male part 8 via a friction weld 19, which can be produced in a per se known manne . 20 indicates a second friction weld between a female joint part and a sim lar tubular member together making up: the second drill rod 7.

Normally a dr ll rod includes a tubular part having a male part at one end and a female part at the other end. It is, however, also possible that drill rods have exclusively male parts or female parts at both ends.

21 indicates a third friction weld wherein the member to be connected to the second drill rod 7 is a part of the female joint part only.

The steps of welding together different parts into a completed, drill rod is advantageous, since a relatively small complicated part of a component can b manufactured separately in a conventional machine i a conventional machining process. Numeral 18 n Fig. 2c indicates a sealing arrangement in the form of a sealing ring, for example of synthetic material , which is arranged to seal an inside opening slot 30 being formed between the two drill ods € and 7 during

operation. It is also possible to arrange a similar or different seal at an outside opening slot being formed between the joint parts. The sealing arrangemen can be arranged with a slit (o slits) or diminutive holes for allowing a minor leakage o flushing fluid flowing in the central flushing channel for providing limited flushing of the coupling parts of the joint,

It is possible to arrange and position both; the axial coupling means and the rotation torque transfer means inverted such tha the first rotation torque transfer means are

arranged at th inside of the male part and the second

rotation torque transfer mean are arranged at an outside of a portion of the female part {but inside said annular space or compartment) receiving the male part. The first axial coupling means can. be arranged at the outside of the male part and the second axial coupling means at the inside of the female part.

It is also possible to arrange the female and male parts such that both the axial coupling means and the rotation torque tx-ansfer means of one of the parts are on the same side. In that case, the female part can be constructed without an annular space or compartment receiving the male part.

Pigs. 3a ~ d show another joint embodiment, wherein the axial coupling means are constructed differently. As can be seen on Pig, 3a, a male part 8 of a drill string component 6 has a plurality of axially extending splines constituting (first) rotation torque transfer means. The plural splines are evenly distributed around part of the length of the male part and are adapted for co-operation with corresponding plural splines constituting second rotation torque transfer¹ means in an inside of a femal par {7 in Figs. 3b ~ d) .

At a distal regio of. the male part 8, from the m parte of the splines, there are radially protruding portions 32 constituting (first) axial coupling means. These (first) axial coupling means in the form of protruding portions are adapted for co-operation between surfaces 33, directed axially from the distal end Of the male part, and corresponding surface portions 35 in a recess or recesses 34, constituting second axial coupling means, formed inside of a mating female part (see in particular Fig. 3d} .

Pig. 3b shows the male part 8 slightly entered into the female part 9, the protruding portions 32 being entered between ridges of the splines 14. Grooves between the spline ridges ar deepened and measured to allow the protruding portions to be moved all the way to the completed

interconnected state prevailing during drilling when the impact surfaces 10 and 11 meet. This state is shown on Fig. 3c and more clearly yet on the partly cut perspective view Fig. 3d. On such deepened groove is referenced with 36 on Fig. 3d.

Figs. 3a - d basically illustrat a variant having a bayonet-like coupling being used instead of a threaded

coupling making up the first and second axial coupling mean© as illustrated in Figs. 2a - c. In order to reach the position in Pig. 3d, after having been fully inserted into the female part 9, the male part 8 has been rotated such that the

surfaces 33 face the surfaces 35 inside the recess 34. Further rotation is prevented because of contact between the splines 12 on the male part reaching contact with the splines 14 inside the female part.

The bayonet- ike coupling can be axxanged for

interlocking axial coupling means either as a result of forward rotation, used, during drilling or as a result of reverse rotation, interlock of the axial coupling -weans results in that the drill, string can b extracted from the hole after completed drilling.

46 indicates two sealing rings that are received in surrounding grooves being provided on a circular cylindrical extension at a distal, end region of th male joint part 8. The sealing rings 46 constitute a sealing arrangement in this embodiment, where the female part is of a one wall type. The sealing rings contact and provide sealing co-operation

together with a circular cylindrical sealing surface 47 inside a proximal portion of the female joint part 9.

In case of interlocking axial coupling means as a result of. forward rotation, used durin drilling, it is important that there is sufficient play between the surfaces 33 and 35 suc that relative movement between the male and female, parts is not obstructed or even come into contact with each other for the reasons explained above.

Aft important feature of the invention is shown in the radial section Fig. 2ci, wherei an angle β is illustrated, being an angle between a radius. R of th join arid a flank direction f , being a line forming a right angle against a main, or central,, flank surface of the rotation torque

transfer means (here being splines) as seen in a radial section.

Two meeting splines are indicated 39 and 40. The radius R extends through a contact region of meeting surfaces

contacting each other at an angle β as defined above through the region of contac between the two meeting flank surfaces of the splines 39 and 40 and a plane SP along the surfaces at the region of contact. A rotational direction is indicated with RD. The angle β is great enough and preferably 45° - 90° more preferred 60° - 90° and most preferred 70° - 90° to avoid excessive wear as well as self locking tendencies in a rotational direction when th joint is subjected to rotation torque for drilling.

The embodiment in Figs. 2a - c is an example, wherein a considerabl al separation of fo example 100 mm is

possible after having established the axial coupling through the axial couplixig means.. The embodiment in Figs. 3a - d is an example of forward lockin (locking during forward rotation) , wherein a smaller axial separation of for example 2 - 4 mm is possible after having established the axial locking through the axial coupling means.

Fig. 4 shows spline© 1.2 extending on a male part 8 forming a helix angle a with respect to an axial direction. This may be advantageous in order to obtain a very slight contracting effect onto meeting drill rods as an effect of forward rotation. The helix angle c* must, however, be small enough such that the mutual movement between the parts is not at all restricted or leading to wear, limited working life or fatigue failure.

For that reason the helix angle « must be so small that there is no risk of inducing any self- ocking effect between the first and second rotation torque, transfer means in order to avoid reduction of the beneficial effects of the invention. This is normally achieved when the helix angle a is between 0^C and 20°.

As is illustrated in Fig. , for variants of splines having a helical path, the flank direction fi also forms an angle a to a cross sectional plane CP through the joint part (~s) . The resulting angle of the flank direction has to be calculated considering both and 0 ,

Figs. 5a, b and c show a variant where the splines X2 on a male part 8 are arranged with hook-like abutments 3? for preventing separation when the drill string components are rotated in one direction. The hook-like abutments 37 co~ operate with contact surfaces 38 at ends of splines 14 inside the female part 9, which is shown partially cut, so as

together m ke up the first and the second axial coupling ^•means. Fig. 5b shows a relative rotational position between th male and the female part constituting locked position* where the hook-like abutment 37 co-operate with contact surfaces 38. Pig. 5c shows a relative rotational position between the male and the female part constituting an unlocked position, where the hook-like abutments 37 are free from contact with the contact surfaces 38.

Fig. 5d diagrammatically illustrates a further variant where the splines 12 on a male part are arranged with hooklike abutments 37 being completed with upstanding uga 51 so as to give an inverted J~shape. This prevents separation when the drill string components are relatively rotated in both directions when a corresponding lug 52 at the bottom en of each female part spline 1 is engaged in a compartment limited by the lug 51 on the male part.

In advantageous and preferred embodiments, the

arrangements in Figs. 3a - d, and 5 with differently shaped and functioning co-operating hook- like abutments and contact surfaces are combined with the arrangement described in relation to Pigs. 2 ~ 2c.

One example of this is illustrated on Fig. 6 wherein the joint parts on the one hand are provided with short threads

13, 15 constituting first axial security coupling means on the male part and second axial security coupling means on the female part, furthermore, and on the other hand, there is also arranged co-operating hook-like abutments and contact surfaces on protruding portions 32 and in recesses 34 constituting first and second axial engagement means oh the male and the female part respectively. Hereby the combinatory effect of the first and second axial coupling means including axial security coupling means as well as axial engagement means, the

Significance of which being explained above, is obtained.

Figs. ?a and b illustrate a variant of axial coupling means shown in Figs. 3a - d being axial security coupling means. After the joint parts have been rotated relative to each other, to the position illustrated in Fig. 7a, and have been axial ly displaced relative each other to the position illustrated in Fig. 7b, eac protruding portion 32 is

positioned i a seat 44 having an axial stop {not shown) for the protruding portion 32 and a rim element 45 preventing unintentional rotational movement of the protruding portion 32 and thereby rotational displacement of the joint parts. During lifting of the drill string, this embodiment provides

increased security against unintentional disassembly compared to the common embodiment of Figs. 3a - d.

When the parts are being pressed together again {back to Fig. 7a> and the male part has bee rotated in a release direction according to the arrow 40 in respect of the female part, the parts can be dismounted by the protruding portions 32 being free t pass the full grooves $ between the splines 50.

Fig. Ba shows an axial section, Fig. 8b a sectioned perspective vie and Fig, Sc a cross section of an assembled joint with the male part 8 fully inserted into the female part 9 and the. male slines 12 in engagement with the female splines 14.

In this embodiment, a rod-shaped element 53 extends from a. rod base 55 adjoining to the inside of the pipe-shaped part 56 of the female part . This is in contrast to the embodiment shown in Fig. 6 and described above where an inner sleeve- shaped member of the female part at a distal region provides a male tread. Furthermore ega ding the embodiment in Fig. 8a, at its distal region, the rod- shaped element 53 is formed with a cup- shaped structure 54 with a cavity 57 , an opening of which facing away from th rod base. At its outside, the cup-shaped structure 54 carries a male thread 60 being female part

(second) axial security coupling means of the second axial coupling means.

The cup- shaped structure 54 is provided with a plurality of first through holes 58 for flushing fluid. The rod base, which extends from the rod-shaped element radially outwards to pass over to the inside of the tubular outside of the pipe- shaped part 56, is provided with a plurality of second through holes 5S: for flushing fluid..

The male part 8 exhibits a sleeve shape and extends from a proximal region being adjoining to the evenly pipe-shaped part, of drill string component to a distal region having on its insid a female thread 61 corresponding to the male thread 60 (male part (first) axial security coupling means of the first axial coupling means} together forming the

security coupling means of the second axial coupling means.

The passage between the female thread 61, the inside 62 of the sleeve shape and the outside surface of the rod- shaped

elements form together with the holes 58 and 59 an effective flushing fluid path. During operation, small amounts of flushing fluid leaks out in each and ever joint passed the splines 12, 14 for cooling purposes, and out between a an outside surface of a cylindrical guiding part 63 most proximal on the on the male part and an insid surface of a cylindrical guiding part 64 most distal on the on pipe-shaped part of the female part and subsequently between shoulder contact surfaces at 65 between impacts.

These inside and outside surfaces 63 and 64 of the male and the female parts respectively contribute to the alignment of the joint during operation. Furthermore, alignment of the joint is also advantageously effected through .cooperation heween radially outwardly directed surfaces: 72 on the

abutments 37 and an inside surface 71 inside the pipe-shaped part of the female part (see Pigs. 8a, 8®, 9b and 10b) . h radially outwardly directed surfaces 72 of the abutments 3 together form an interrupted annular envelope surface.

Ensuring proper contact between the surfaces 71 and 72 can. be arranged by having a slightly smaller inside diameter of a portion of the female part forming the inside surface 71, Ensuring proper contact between the surfaces 71 and 72 can alternativel be arranged by having a slightly larger outside diameter of the abutments {and the radially outwardly directed surfaces 72) .

This combined guiding arrangement at two axially

separated positions f th joint is advantageous for achieving stable ighmen .

The complete female part includes a rod portion

comprising the rod-shaped element 53> the rod base 55 and a portion 56' of th pip -shaped par as shown in Pig 8d

together with a continuation 56" of the pipe-shaped part as shown in Fig. 8e. Th portion 56' is friction welded at 66^'"^* to a meeting surface at 66' of the continuation 56^*" to form a weld 66 of the complete female part. The female part is subsequently in turn friction welded to a pipe of the drill string component .

Furth more, inside the continuation 56" there are positioned female part splines 14, At the inside end of each sline 14 there are provided contact surfaces 38 constituting female part axial engagement, means (compare 38 in Figs. 5a - c) .

Figs. 9a and b illustrates the male part of the

embodiment of Fig. 8a, From the side view i Fig. 9b is evident that abutments 37 are arranged free from the ap.lin.es such that an annular groove can foe said to be provided

therebetween. This facilitates production and fine machining of contact surfaces on the abutments 37. The contact surfaces 37' are arranged for engagement in one rotational direction only with contact surfaces 38 constituting femal part axial engagement means (see Fig. 8e) . It is referred to the

description above of different elements for full understanding of the male part. The male part is friction welded to a. pipe forming the main part of a drill string component.

Figs. 10a and b illustrates an alternatively configured male part. From the side view i Fig. 9ta is evident that abutments 37 have contact surfaces 37^* are arranged for engagement in a first rotationa direction with contact surfaces 38 constituting female part axial engagement means {see Fig. 8e) . This alternatively configured male part, however, has abutments 37 arranged so as to have contact surfaces 37" that are arranged for engagement also in a second rotational direction with contact surfaces 38

constituting female part axial engagement means (see Fig, 8e) .

Furthermore_* in this male part embodiment, there is no inner female thread making up a male part axial security coupling irneahs most d ©tally inside the surface 62. Axial engagement thus relies fully on the axial engagement means.

The embodiment in Figs. I0a and b is particularly applicable for a shank adapter 67, see Fig. 11, where axial security coupling means would be an obstacle because of the repeated assembly, disassembly taking place between the shank adapter and the most adjacent drill string component, 68 indicates a male part as shown and described with reference to Figs. 10a and b. 69 indicates a drillin machine end of the shank adapter and 70 indicates an inside component of a swivel . It is possible to use other means preventing rotation between interconnecteel parts besides splines as first and second rotation torque transfer means. Basically,

interconnected parts having rotation preventing means that engage each other can be made in various conf gurations when they fulfil the requirements explained above. Use of splines is, however, preferred, for number of reasons such as ease of production and reliability. The number of splines can be adapted to the situation and if the joint parts have to be relatively rotated for achieving axial locking. The axial length of the splines is chosen so as to reach an acceptable surface load on th flanks of the splines.

The embodiments shown in the Pigs, illustrate drill strings having th male joint part of a joint being carried by a drill string component being closest to the drill hammer but it should be evident that the opposite situation with the female joint part being carried by the drill string component being closest to the drill hammer is fully possible.

The term comprised is here intended as a open (and not closed) definition which is not restricted to the feature following the term, Also other features can b present.

Claims

C L A I M S

1. Joint tor joining together drill st ing components (6,7) for percussion drilling, wherein each drill st ing component extends along an xial direction (A)., and wherein, in

Operation, impact shock waves and rotation torque are arranged to be transferred via the joint, the joint including a male part (8) and a female part (9) having meeting impact surfaces (10, 11) ,

characterized in

- that the male part (8) exhibits:

. first rotation torque transfer means (12) , and

ii. first axial coupling means (13),

- that the female part (9) exhibits:

ii.i. second rotation torque transfer means (14), and

iv. second axial coupling means (15) ,

~ wherein the first and second rotatio torque transfer means (12,14) extend on th respective male and female parts such, and

- wherein the first and second axial coupling means (13,15) are posi oned such,

that when the drill string is subjected to rotation torque for drilling, relative axial movement is allowed between the male (8) and the female (9) parte when being in a interconnected state of co-operation betwee the firs and second rotation torque transfer means.

2. Joint according to claim 1, characterised in that the first and second rotation torque transfer means (12,14) are mating splines having contacting surfaces that extend in parallel with said axial direction (A) on the respective male (8) and female (9) parts or extend helically on the respective male and female parts, at a helix angle (a) between 0* and 20° to the axial direction.

3. Joint according to claim 2, characterized in that the first and second axial coupling means include axial engagement means formed b radially directed protrusions on one of the wale and the female parts.

4. Joint according to claim 3 , characterized in that the axial engagement means includes radially directed protrusions in the form of hpok elements or abutments on one of the male and the female parts for engagement with abutment surface portions on the other one of the male and the female parts.

5. Joint according to claim 3 or 4, characterized in that when the male (8) and the female (9) parts are interconnected, the axial engagement means are arranged to engage in forward rotation of the drill string and/o reverse rotation of the drill string and thereby limit relative axial movement between the male and the female part.

6. Joint according to any one of claims 2 - 5, characterized in that one of the first and second axial coupling means

^'{13, IS), is constituted by end surfaces f splines on the male (8) or female {9} part.

7. Joint according to any one o the previous claims,

characterized in that the first and second axial coupling means include axial security coupling means,

8. Joint according to claim 7, characterised in, that the axial security coupling means include a thread coupling or a bayonet coupling.

S. Joint according to claim 7 or 8, characterized in that second axial security coupling means in the form of outside threads are positioned at a distal portion of a sleeve-shaped or rod-shaped element extending centrally of the female part and that mating first, axial security coupling means in th form of inside threads are positioned at. a distal portion of the wale part.

10. Joint according to any one of claims 1 - 9, characterized in that the female part (9) includes an inner and an outer wall, together defining an annular compartment for the reception of a sleeve-formed male part.

11. Joint according to claim 10, characterized in that the first rotation torque transfer means is positioned on one of the inside and the outside of the sleeve-formed male ^

12. Joint according to claim 10 or 11, characterised in that the first axial coupling means is positioned on one of the inside and the outside of the sleeve- ormed male part.

13. Joint according to any one of claims 1 - 12, characterised in that a sealing arrangement {18} is positioned at an inside opening slot formed between the male (8) and the female (θ) parts, as seen in an operative position with the first and second impact surfaces close to each other.

14. Joint according to any one of claims 1 - 13, characterized in that the first and second impact surfaces (10, 11; 16, 17) are arranged for one from the group: shoulder drive, bottom drive and dual drive.

15. Joint according to claim 14, wherein the first and second impact surfaces (10, 11; 16, 17) are arranged for shoulder drive, characterized in that outside surfaces of meeting drill string components, at least in the region of the joint, form an.

essentially continuous envelope surface.

16. Joint according to any one of claims 1 - 15, characteriaed in that the female part is sleeve-shaped having both the second rotation torque transfer means and the second axial coupling means being oriented o an inside sleeve wall.

17. Joint according to an one of claims 1 - 16, characterized in that an angle {(5) between a radius (R) of the joint parts and a flank direction {f) forming a right angle against a main surface of the rotation torque transfer means is 60^δ - 90" and more preferably 70* - 90^s.

18. Joint according to any one of claims l ·· 17, characterized in that the male part externally as a proximal, cylindrical guide portion for co-operation wit an internal, cylindrical guide surface a a distal portion of the female part .

19. Joint according to any one o claims 1 - 18, characterized in that the male part at a distal region, has part cylindrical outside guide surfaces for co-operation with an internal, cylindrical guide surface at a proximal portion of the female par ,

20. Mal part {ø) of a joint for joining together drill string components (6,7) for percussio drilling, wherein each drill string component extends along an axial direction, and

wherein, in operation, impact shock wayee and rotation torque are arranged to be transferred via the joint, wherein the male part. (8) is part of a first, drill string component {€.) and is arranged to co-operate with a female part of a second drill string component, and wherein an impact surface o the wale part is arranged to ep operate with an impact surface on the female part,

characterized in

- that the male part (8) exhibits:

i. first rotation torque transfer means (12), and

i. first axial coupling means (13),

for co-operation with

iii. second rotation torque transfer means, and

iv. second axial coupling means,

on the female part (9),

- wherein the first rotation torque transfer means for contacting the second rotation torque transfer means extend on the male part such, and

- wherein the first axial coupling means for co-operation with the second axial coupling means is positioned such,

- that whe the drill strin is subjected to rotation torque for drilling, relative axial movement is allowed between the male (8) and the female {9} parts when being in an

interconnected state of co-operation between the first and second rotation torque transfer means.

21. Female part (9) of a joint for joining together drill string components for percussion drilling, wherein each drill string component extends along an axia direction, and

wherein, in operation, impact shock waves and rotation torque are arranged to be transferred via the joint, wherein the female part (9) is par of a second drill string component (7) and is arranged to co-operate with a male part of a first drill string component, wherein a second impact surface on th female part is arranged to co-operate with firs impact surface on the male part,

characterized in

- that the female part (9) exhibits:

i. second rotation torque transfer means (1.4), and

ii. second axial coupling means (15),

for co-operation with

iii. first rotation torque transfer means, and

xv. first axial coupling means,

on the male part (8) ,

- wherein the second rotation torque transfer means for contacting the first rotation torque transfer means extends on the female part such, and

- wherein the second axial coupling means for co-operation with the first axial coupling means is positioned such,

- that, when the drill string is subjected to rotation torque for drilling, relative axial movement is allowed between the male (8) and the female (9) parts when being in an

interconnected state of co-operation between the first and second rotation torque transfer means.

22. Drill rod (6; 7) for percussion rock drilling,

characterized in that the drill rod includes at least one male part (8) of a joint according to claim 20.

23. Drill rod (6; 7) for percussion rock drilling,

characterized in that the drill rod includes at least one female part (9) of a joint according to claim 21.

24. Drill rod according to claim 22 or 23, wherein the first and second impact surfaces (10, 11; 16, 17) are arranged for shoulder drive, characterized tn that outside surfaces of joint parts of co-operating drill rods are formed such that at least in the region of the joint they form an essentially continuous envelope surface.

25. Shank adapter (5) for rock drilling machine (1), characterized in that th s ank adapter {5} includes a m le part of a joint according to claim 23 or a female part of a joint according to claim 24.

26. Shank adapter according to claim 25, characterized in that the shank adapter is provided with axial engagement means that are arranged to engage in forward as well as reverse rotation of the drill string and thereby limit relative axial movement relative to an attached and engaged drill string component.

27. Method for joining together drill string components (6,7) for per-cussion drilling, wherein each drill string component extends along an axial direction (A), and wherein, in

operation, impact shock waves and rotation torque are

transferred via a joint, including the steps of:

- initiating axial insertion of a male part (8) of a first drill string component into a female part (9) of a second drill string component,

- rotate the first drill string component relative to the second drill string component to ensure engagement of axial security coupling means in the form of a thread coupling or a bayonet coupling,

- continue axial insertio of the male part (8) into the female part (9) a determined distance whereby the first drill string component is allowed to rotate relative to the second drill string component to ensure engagemen of axial

engagement means and to ensure engagement of first and second rotation torque transfer means (12,14) arranged on the

respective male and female part.