EP3553270B1 - Druckfluidströmungssystem für einen dth-hammer und normalzirkulationshammer auf basis davon - Google Patents

Druckfluidströmungssystem für einen dth-hammer und normalzirkulationshammer auf basis davon Download PDF

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Publication number
EP3553270B1
EP3553270B1 EP17880617.0A EP17880617A EP3553270B1 EP 3553270 B1 EP3553270 B1 EP 3553270B1 EP 17880617 A EP17880617 A EP 17880617A EP 3553270 B1 EP3553270 B1 EP 3553270B1
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Prior art keywords
pressurized fluid
drill bit
piston
chamber
hammer
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EP17880617.0A
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English (en)
French (fr)
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EP3553270A4 (de
EP3553270A1 (de
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Jaime Andres Aros
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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/06—Down-hole impacting means, e.g. hammers
    • E21B4/14—Fluid operated hammers
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B10/00—Drill bits
    • E21B10/36—Percussion drill bits
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B10/00—Drill bits
    • E21B10/36—Percussion drill bits
    • E21B10/38—Percussion drill bits characterised by conduits or nozzles for drilling fluids

Definitions

  • the present invention relates generally to pressurized fluid flow systems for percussive mechanisms operating with said fluid, particularly for DTH (Down-The-Hole) hammers and more particularly for normal circulation DTH hammers, and to DTH hammers with said systems.
  • DTH Down-The-Hole
  • DTH hammers which are widely used in the drilling industry, in mining as well as civil works and the construction of water, oil and geothermal wells.
  • the DTH hammer of cylindrical shape, is used assembling it on a drill rig located at ground surface.
  • the drill rig also comprises a drill string comprising rods assembled together, the rear end, understood as the end that is farther to the hammer drill bit (elemtent described further along in these specifications), being assembled to a rotation and thrust head and the front end, understood as the end that is closer to the hammer drill bit, coupled to the hammer.
  • the drill rig supplies the necessary pressurized fluid to the hammer for the hammer to operate.
  • the main movable part of the hammer is the piston.
  • This member of the hammer has an overall cylindrical shape and is coaxially and slidably disposed in the inside of a cylindrical outer casing.
  • the piston When the hammer is operative in the mode known as "drilling mode", the piston effects a reciprocating movement due to the change in pressure of the pressurized fluid contained in two main chambers, a front chamber and a rear chamber, formed inside the hammer and located at opposite ends of the piston.
  • the piston has a front end in contact with the front chamber and a rear end in contact with the rear chamber, and has outer sliding surfaces or sliding sections of the outer surface of the piston (as opposed to sections with recess areas, grooves or bores) and inner sliding surfaces or sliding sections of the inner surface of the piston (again as opposed to sections with recess areas, grooves or bores).
  • the outer sliding surfaces are mainly designed for ensuring guidance and aligment of the piston within the hammer. Besides, in most hammers these surfaces, together with the inner sliding surfaces of the piston, in cooperation with other elements as described further along in these specifications, permit control of the alternate supply and discharge of pressurized fluid into and from the front and rear chambers.
  • the foremost part of the hammer, which performs the drilling function, is known as the drill bit and it is slidably disposed on a driver sub mounted in the front end of the outer casing, the drill bit being in contact with the front chamber and adapted to receive the impact of the front end of the piston.
  • a component known as drill bit guide is normally used, which is disposed in the inside of the outer casing.
  • the rotating movement provided by the drill rig is transmitted to the drill bit by means of fluted surfaces or splines in both the rearmost part o the drill bit (or shank) and the driver sub.
  • the drill bit head of larger diameter than the outer casing and than the drill bit shank and driver sub, has mounted therein the cutting elements that fulfill the drilling task and extend forward from the drill bit front face.
  • the movement of the drill bit is limited in its rearward stroke by the driver sub and in its forward stroke by a retaining element especially provided for said purpose.
  • a rear sub is provided that connects the hammer with the drill string and ultimately to the source of pressurized fluid.
  • the rear end of the hammer is understood to be the end where the rear sub is located and the front end of the hammer, the end where the drill bit is located.
  • the respective sequence for the states of the front and rear chambers are the following: [a - b(expansion) - c - b(compression) - a] and [c - b(compression) - a - b(expansion) - c].
  • the transition from one state to the other is independent for each chamber and is controlled by the position of the piston with respect to other parts of the hammer in such a way that the piston acts in itself as a valve, as well as an impact element.
  • a first operative mode or "drilling mode” when pressurized fluid is supplied to the hammer and the hammer is in the impact position, the piston immediately begins the reciprocating movement and the drill bit is impacted in each cycle by the piston, the front end of the drill bit thereby peforming the function of drilling the rock at each impact.
  • the rock cuttings are exhausted to the ground surface by the pressurized fluid discharged from the front and rear chambers to the bottom of the hole.
  • the magnitude of the pressurized fluid column with rock cuttings also increases, producing a greater resistance to the pressurized fluid discharge from the chambers. This phenomenon negatively affects the drilling process. In some applications the leakage of water or any other fluid into the hole increases even more this resistance, and the operation of the hammer may cease.
  • this operative mode of the hammer can be complemented with an assisted flushing system which allows discharge of part of the flow of pressurized fluid available from the source of pressurized fluid directly to the bottom of the hole without passing through the hammer cycle.
  • the assisted flushing system allows the hole to be cleaned thorougly while it is being drilled.
  • a second operative mode of the hammer or "flushing mode” the drill string and the hammer are lifted by the drill rig in such a way that the drill bit loses contact with the rock and all the pressurized fluid is discharged through the hammer directly to the bottom of the hole for cleaning purposes without going through the hammer cycle, thus ceasing the reciprocating movement of the piston.
  • the pressurized fluid coming from the assisted flushing system has an energy level substantially similar to that of the pressurized fluid coming out from the source of pressurized fluid, as opposed to what happens with the pressurized fluid exhausted from the chambers, which is at a pressure substantially lower due to the exchange of energy with the piston.
  • the drill bit or a cylindrical sealing element of the hammer which has a diameter substantially similar to the diameter of the drill bit head and larger than the external diameter of the outer casing, performs the function of preventing the leakage of pressurized fluid and rock cuttings into the annular space between the hammer and the wall of the hole and between the drill string and the wall of the hole when the hole is being drilled (as happens with a normal circulation hammer), forcing these cuttings to travel through the sampling tube and drill string to the ground surface by the action of the pressurized fluid. If it is the drill bit that performs this sealing function, it has a peripherial region that isolates the front face of the drill bit from said annular space.
  • Different pressurized fluid flow systems are used in hammers for the process of supplying the front chamber and the rear chamber with pressurized fluid and for discharging the pressurized fluid from these chambers.
  • a supply chamber formed inside the hammer from which, and depending on the position of the piston, the pressurized fluid is conveyed to the front chamber or to the rear chamber.
  • the piston acts as a valve, in such a manner that depending on its position is the state in which the front and rear chambers are, these states being those previously indicated: supply, expansion-compression and discharge.
  • the net force exerted on the piston is the result of the pressure that exists in the front chamber, the area of the piston in contact with said chamber (or front thrust area of the piston), the pressure that exists in the rear chamber, the area of the piston in contact with said chamber (or rear thrust area of the piston), the weight of the piston and the dissipative forces that may exist.
  • the greater the thrust areas of the piston the greater the force generated on the piston due to a certain pressure level of the pressurized fluid and greater the power and energy conversion efficiency levels which can be achieved.
  • Type A Flow System represented by patents US4084646, US5944117 and US6135216
  • the designs described in these patents comprise a cylinder mounted inside the outer casing, the cylinder creating a fluid passageway between the outer surface of said cylinder and the inner surface of the outer casing.
  • This fluid passageway extends along the rear half of the piston and ends in the supply chamber, which is partially defined by the outer sliding surface of the piston, near its middle point, and the inner surface of the outer casing.
  • the provision of this cylinder requires the use of a dual outer diameter piston, the outer diameter of the same being greater at its front end and smaller at its rear end where the cylinder is placed.
  • an air guide is provided for controlling the discharge of the rear chamber, the air guide being a tubular element coaxial with the piston and the outer casing and located at the rear face of the rear chamber.
  • a footvalve is provided in order to control the discharge of the front chamber, the footvalve being a hollow tubular element coaxial with the piston and the outer casing and emerging from the rear face of the drill bit, known as impact face.
  • Type B Flow System represented by patents US5984021, US4312412 and US6454026
  • the designs described in these patents comprise a pressurized fluid supply tube (inside of which the supply chamber is generated), which extends from the rear face of the rear chamber and is received inside a central bore in the piston. This bore extending along the whole length of the piston.
  • the supply tube interacts with bores and undercuts inside the piston.
  • the front thrust area of the piston is highly reduced due to the fact that a sufficiently large impact area is still required in order to withstand the stress generated by the impact, thus taking away surface from the front thrust area.
  • a supply tube requires the use of a piston having a central bore extending along its entire length, resulting in the effects on power already mentioned for the Type A system.
  • the design described in this patent has three different sets of supply passages built in the outer casing.
  • the first set of passages end at the inner surface of the outer casing and create a supply chamber between the outer sliding surface of the piston and the inner surface of the outer casing.
  • the second and third sets of passages allow for the flow of pressurized fluid from the supply chamber toward the front chamber and toward the rear chamber respectively.
  • the supply chamber interacts with recesses in the outer sliding surface of the piston and with the second and third sets of passages in the outer casing, while the discharge of the front chamber and the rear chamber are respectively controlled with the use of a footvalve and an air guide (refer to the Type A flow system applied to a normal circulation hammer).
  • Type D Flow System represented by patents US5113950 and US5279371
  • a supply chamber is provided in the rear end of the piston, the designs have similar characteristics to the Type A and Type B flow systems.
  • the Type D flow system uses a central supply tube as in the Type B flow system, but differs from the latter in that the supply chamber is not created inside the supply tube. Instead, similarly to the Type A flow system, the supply chamber is created and acts on a portion of the rear end of the piston. In this manner the supply tube performs the function of helping to convey the pressurized fluid toward the supply chamber and does not participate in its creation. All this produces as a consequence a reduction in the piston's rear thrust area.
  • the need to discharge the rear chamber requires the use of a piston with a central bore that emerges on the front face of the same, thus reducing even more the rear thrust area and the front thrust area of the piston, which results in a cycle of even less power.
  • the designs described in these patents comprise a cylinder mounted inside the outer casing, the cylinder creating a supply chamber for supplying pressurized fluid to the front chamber and to the rear chamber of the hammer, and a discharge chamber for discharging pressurized fluid from the front chamber and from the rear chamber.
  • the supply and discharge chambers are defined by respective recesses, disposed in series longitudinally, on the inner surface of the outer casing.
  • Type 1 Flow System represented by the patents US5154244, RE36002(US), US6702045 and US5685380
  • Type A and Type D flow systems From the point of view of the control of the state of the front and rear chambers, commercial designs from these patents are of the Type A and Type D flow systems.
  • a front region of the piston of smaller diameter that interacts with a piston guide is used as an alternative solution to the footvalve for controlling the discharge of the front chamber.
  • the discharge of the rear chamber is controlled by means of an air guide that opens or blocks the flow of pressurized fluid from the rear chamber to a central coaxial channel formed between the inner sliding surface of the piston and the outer surface of the sampling tube, this passage extending from the rear chamber to the rear end of the drill bit.
  • the disadvantages of this flow system are the same ones as those associated with the Type A and Type D flow systems and, in particular, impact negatively the design of the drill bit in two aspects.
  • the first one is the need for a multiplicity of manufacturing processes for producing the channels in the outer surface of the drill bit, which increases the manufacturing cost of the hammer.
  • the second is that, due to the presence of these channels, the drag surface of the splines, which depend on the contact area of each spline individually and the total number of splines, can in some applications be insufficient.
  • This last problem can be counterbalanced by lengthening the drill bit, but this implies increasing the cost of the hammer.
  • Patents US5407021 and US4819746 describe a flow system where the pressurized fluid is conducted from the rear end of the drill bit up to an intermediate point on the outside surface of the same by means of channels formed in a cooperative way by splines machined on the inner surface of the driver sub and splines machined on the outer surface of the drill bit shank. From this intermediate point the flow of pressurized fluid is deviated through mainly longitudinal bores created in the head of the drill bit in such a way as to discharge the pressurized fluid at the peripheral region of the front end of the drill bit.
  • the bit head has the further function of avoiding the escape of pressurized fluid through the annular space formed between the hammer and the wall of the hole and between the rods and the wall of the hole.
  • patent US4819746 has a Type A flow system.
  • a front portion of the piston of a smaller diameter is used that interacts with a piston guide, as described in the Type B flow system.
  • the discharge of the rear chamber is controlled by an air guide ( US4819746 ) which opens or closes the flow of pressurized fluid from the rear chamber to a central coaxial channel formed in between the inner sliding surface of the piston and the outer surface of the sampling tube, which extends up to the rear end of the drill bit.
  • an air guide US4819746
  • the pressurized fluid flow system of the invention is characterized by comprising a set of equal diameter outer sliding surfaces for the piston thus avoiding failure of this part due to thermal cracks induced by friction between the piston and misaligned parts (air guide, supply tube, foot valve, etc.). Moreover, the piston does not have holes, channels or passages, making it a completely solid component.
  • the pressurized fluid flow system of the invention is characterized by having a cylinder coaxially disposed in between the outer casing and the piston; and two sets of channels, a set of supply channels and a set of discharge channels, delimited by the outer surface of the cylinder and the inner surface of the outer casing.
  • the set of supply channels is permanently filled with fluid coming from the source of pressurized fluid and connected without interruption to the outlet of said source.
  • the set of discharge channels is permanently communicated with the bottom of the hole drilled by the hammer.
  • the supply channels are disposed in parallel longitudinally with respect to the discharge channels overlapping longitudinally and both sets of channels are defined by respective sets of recesses on the cylinder outer surface.
  • the piston has a recess on its external surface that defines, in cooperation with the inner surface of the cylinder, a supply chamber.
  • the supply chamber is permanently connected without interruption to the set of supply channels. In this way, the supply chamber is permanently filled with fluid coming from the source of pressurized fluid and connected without interruption to the outlet of said source.
  • the flow of pressurized fluid supplied into and discharged from the front and rear chambers is controlled solely by the overlap or relative position of the outer sliding surfaces of the piston with the inner suface of the cylinder.
  • front and rear sets of recesses are provided on the cylinder.
  • the flow of pressurized fluid into and out of the front and rear chambers takes place inbetween the inner surface of the cylinder and the outer surface of the piston. Further, the state of the front chamber and the rear chamber are controlled in the invention by the interaction of a single pair of components.
  • the front thrust area and the rear thrust area of the piston under the configuration of the invention are identical in size. Additionally, control of the discharge of the front chamber and the rear chamber by interaction between the piston and the cylinder makes it unnecessary to have either a foot valve or a front portion of the piston of smaller diameter interacting with a piston guide or an air guide for this purpose, thus avoiding the additional losses in the thrust areas as it occurs with the flow systems of the prior art.
  • one or more flushing channels may be provided in the dividing walls that separates the set of supply channels and the set of discharge channels for permitting part of the flow of pressurized fluid available from the source of pressurized fluid to be discharged directly to the bottom of the hole, conforming in this fashion an assisted flushing system and enabling an increased deep drilling capacity without a noticeable reduction in the penetration rate.
  • the invention also refers to a normal circulation DTH hammer characterized by having the above-described pressurized fluid flow system and a drill bit in which the conventional central passage in the rear end thereof and the two or more passageways that converge to this central passage used in normal circulation hammers have been replaced by one or more flushing passages bored across the drill bit and extending from the channels which, as in the described Type 1 and Type 2 flow systems, are cooperatively formed by the splines on driver sub and on the drill bit shank, to the front face of the drill bit.
  • This enables a simplified and sturdier drill bit for a normal circulation hammer.
  • a normal circulation DTH hammer that comprises the following main components:
  • the pressurized fluid flow system of the invention includes a cylinder (40) that is coaxially disposed in between the outer casing (1) and the piston (60), the cylinder (40) having an inner (47) and an outer surface (48).
  • the rear chamber (230) of the hammer is defined by the rear sub (20), the cylinder (40) and the rear thrust surface (62) of the piston (60).
  • the volume of the rear chamber is variable depending on the piston's (60) position.
  • the front chamber (240) of the hammer is defined by the drill bit (90), the cylinder (40), the drill bit guide (150) and the front thrust surface (63) of the piston (60).
  • the volume of the front chamber is also variable depending on the position of the piston (60).
  • the piston (60) has an annular recess (68) on its external surface that defines, in cooperation with the inner surface (47) of the cylinder (40), a fluid flow supply chamber (66).
  • This fluid flow supply chamber (66) is respectively longitudinally limited at each end by the outer sliding surfaces (64, 67) of the piston.
  • the cylinder (40) has a set of supply (2) and discharge (3) channels defined by respective longitudinal recesses on its outer surface (48), the supply (2) and discharge (3) channels disposed around said surface (48) for in the first case conveying pressurized fluid from the rear sub (20) to the supply chamber (66) and therefrom to the front (240) and rear (230) chambers and in the second case discharging the pressurized fluid from the front (240) and rear (230) chambers towards the channels (97) formed between the driver sub (110) and the drill bit shank (95) and therefrom towards the bottom of the hole drilled by the hammer.
  • the first of these sets of channels is in permanent fluid communication with the source of pressurized fluid and it is filled with said fluid while the second of these sets of channels is directly communicated with the bottom of the hole.
  • the cylinder (40) has rear pressurized fluid intake ports (41) bored therethrough, which connect the supply channels (2) with a supply undercut (21) in the rear sub (20), and has elongated front pressurized fluid exit ports (42) bored therethrough, which fluidly and uninterruptedly communicate the set of supply channels (2) of the cylinder with the supply chamber (66), therefore permanently filling it with high pressure fluid.
  • the cylinder (40) also has rear (43) and front (44) discharge ports bored therethrough, which allow the pressurized fluid to respectively flow from the rear chamber (230) and front chamber (240) into the set of discharge channels (3).
  • the cylinder (40) further has a front set (45) and a rear set (46) of recesses on its inner surface for allowing the pressurized fluid which flows from the rear sub (20) to the supply chamber (66) through the set of supply channels (2) to respectively divert part of the flow to the front (240) and rear (230) chambers in cooperation with the multiple outer sliding surfaces (64, 67) of the piston (60).
  • the front chamber (240) is in direct fluid communication with the supply chamber (66) through the front set of recesses (45) of the cylinder (40). In this way, the pressurized fluid is able to freely flow from the supply chamber (66) to the front chamber (240) and start the movement of the piston (60) in the rearward direction.
  • This flow of pressurized fluid to the front chamber (240) will stop when the piston (60) has traveled in the front end to rear end direction of its stroke until the point where the front outer supply edge (73) of piston (60) reaches the rear limit of the front set of recesses (45) of the cylinder (40). As the movement of the piston (60) continues further in the front end to rear end direction of its stroke, a point will be reached where the front outer discharge edge (72) of the piston (60) will match the front limit of the front discharge ports (44) of the cylinder (40).
  • the front chamber (240) of the hammer will become fluidly communicated with the set of discharge channels (3) through the front set of discharge ports (44) of the cylinder (40) (see Figure 4 ).
  • the pressurized fluid contained inside the front chamber (240) will be discharged into the set of discharge channels (3) and from the set of discharge channels (3) it is able to freely flow out of the hammer through the channels (97) cooperatively formed between the splines (93) of the drill bit shank (95) and splines (112) of the driver sub (110), and through the flushing passages (92) of the drill bit (90) to the front face (99) of the drill bit (90).
  • the drill bit (90) is aligned to the outer casing (1) of the hammer by a drill bit guide (150) having discharge grooves (151) as shown in the Figures.
  • these discharge grooves connect the set of discharge channels (3) with the channels (97), so that the discharge of pressurized fluid flows through these discharge grooves (151) before reaching the channels (97) and thereafter flows through the flushing passages (92) of the drill bit (90).
  • the invention is not limited to the use of a drill bit guide and alternative alignment solutions may be used with corresponding pressurized fluid discharge means.
  • the rear chamber (230) is in direct fluid communication with the set of discharge channels (3) through the rear set of discharge ports (43) of the cylinder (40) (see Figure 3 ).
  • the pressurized fluid contained inside the rear chamber (230) will be discharged into the set of discharge channels (3) and from the set of discharge channels (3) out of the hammer and to the front face (99) of the drill bit (90) in a similar fashion as with the pressurized fluid discharged from the front chamber (240).
  • the pressurized fluid is able to freely flow out of the hammer and to the front face (99) of the drill bit (90) in a similar fashion as with the pressurized fluid discharged from the rear and front chambers (230, 240) when the hammer is in drilling mode.

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Claims (4)

  1. Ein unter Druck stehendes Fluidströmungssystem für einen normalen Zirkulationshammer im Bohrloch, dadurch GEKENNZEICHNET, daß umfassend:
    ein zylindrisches Außengehäuse (1) mit einem hinteren Ende und einem vorderen Ende;
    ein Treiberunterteil (110), das an dem vorderen Ende des Außengehäuses (1) angebracht ist und eine Innenfläche (113) mit darauf bearbeiteten Keilen (112) aufweist;
    ein hinteres Teil (20), das an dem hinteren Ende des äußeren Gehäuses (1) angebracht ist, um den Hammer mit der Quelle von unter Druck stehendem Fluid zu verbinden;
    einen Kolben (60), der verschiebbar und koaxial in dem äußeren Gehäuse (1) angeordnet ist und aufgrund der Druckänderung des unter Druck stehenden Fluids, das in einer vorderen Kammer (240) und einer hinteren Kammer (230) enthalten ist, die sich gegenüberliegenden Seiten befinden, hin- und herbewegen kann des Kolbens (60), wobei der Kolben (60) mehrere äußere Gleitflächen mit gleichem Durchmesser (64, 67) aufweist;
    einen Bohrer (90), der verschiebbar auf dem Treiberteil (110) montiert ist, wobei der Bohrer (90) hauptsächlich ein Rotationskörper ist und aus einem Bohrerschaft (95) am hinteren Ende des Bohrers und einem Bohrer besteht Kopf (96) am vorderen Ende des Bohrmeißels, wobei der Bohrmeißelkopf (96) einen größeren Durchmesser als der Bohrerschaft (95) hat und am vorderen Ende des Bohrmeißelkopfes eine Vorderseite (99) aufweist; der Bohrerschaft (95) hat eine Außenfläche (98) mit darauf bearbeiteten Keilen (93);
    Kanäle (97), die kooperativ zwischen den Keilen (112) an der Innenfläche (113) des Treiberteils (110) und den Keilen (93) an der Außenfläche (98) des Bohrerschafts (95) gebildet sind;
    einen Zylinder (40), der koaxial zwischen dem äußeren Gehäuse (1) und dem Kolben (60) angeordnet ist, wobei der Zylinder (40) eine innere (47) und eine äußere Oberfläche (48) aufweist;
    eine Versorgungskammer (66), die durch eine ringförmige Aussparung an der Außenfläche des Kolbens (60) definiert ist, wobei diese Versorgungskammer (66) an jedem Ende in Längsrichtung durch die äußeren Gleitflächen (64, 67) begrenzt ist und in ständiger Fluidverbindung steht mit der Druckflüssigkeitsquelle zur Zufuhr von Druckflüssigkeit zur vorderen Kammer (240) und zur hinteren Kammer (230);
    einen Satz von Zufuhrkanälen (2), definiert durch entsprechende Längsaussparungen an der Außenfläche (48) des Zylinders (40), um unter Druck stehendes Fluid vom hinteren Teil (20) zur Versorgungskammer (66) zu befördern, und einen Satz von Auslasskanäle (3), definiert durch entsprechende Längsaussparungen an der Außenfläche (48) des Zylinders (40), zum Ablassen von unter Druck stehendem Fluid aus der vorderen Kammer (240) und der hinteren Kammer (230) zum Boden des zu bohrenden Lochs durch den Hammer durch die Kanäle (97), wobei die Entladungskanäle (3) in Längsrichtung in Bezug auf die Versorgungskanäle (2) parallel angeordnet sind;
    mehrere Einlass- und Auslassöffnungen (41, 42) und hintere und vordere Auslassöffnungen (43, 44), die in dem Zylinder (40) vorgesehen sind, jeweils den Sätzen von Zufuhrund Auslasskanälen (2, 3) zugewandt sind;
    einen vorderen Satz von Aussparungen (45), die an der Innenfläche (47) des Zylinders (40) vorgesehen sind, um die Versorgungskammer (66) mit der vorderen Kammer (240) zu verbinden, wenn diese mit Druckflüssigkeit versorgt werden muss; und
    einen hinteren Satz von Aussparungen (46), die an der Innenfläche (47) des Zylinders (40) vorgesehen sind, um die Versorgungskammer (66) mit der hinteren Kammer (230) zu verbinden, wenn diese mit Druckflüssigkeit versorgt werden muss;
    den in dem Zylinder (40) vorgesehenen vorderen Satz von Auslassöffnungen (44) zum Entladen der vorderen Kammer (240) in den Satz von Auslasskanälen (3); und
    den hinteren Satz von Auslassöffnungen (43), die in dem Zylinder (40) vorgesehen sind, um die hintere Kammer (230) in den Satz von Auslasskanälen (3) zu entladen;
    wobei der Fluss von unter Druck stehendem Fluid in und aus der vorderen und hinteren Kammer (240, 230) ausschließlich durch die Überlappung oder relative Position der mehreren äußeren Gleitflächen (64, 67) des Kolbens (60) und der Innenfläche gesteuert wird (47) des Zylinders (40) während der abwechselnden Bewegung des Kolbens (60) und wobei der Fluss von unter Druck stehendem Fluid in und aus der vorderen und hinteren Kammer (240, 230) zwischen der Innenfläche (47) stattfindet. des Zylinders (40) und der äußeren Gleitflächen (64, 67) des Kolbens (60).
  2. Druckfluidströmungssystem nach Anspruch 1, dadurch GEKENNZEICHNET, wobei der Zylinder (40) einen hinteren Satz von Einlassöffnungen (41) aufweist, damit das unter Druck stehende Fluid von dem hinteren Teil (20) zu dem Satz von Versorgungskanälen (2) fließen kann.
  3. Druckfluidströmungssystem nach Anspruch 1, dadurch GEKENNZEICHNET, Längsaussparungen, aus denen die Sätze von Zufuhrkanälen (2) und Auslasskanälen (3) bestehen, vorzugsweise so angeordnet sind, dass sie sich in Längsrichtung überlappen.
  4. Ein normaler Zirkulationshammer im Loch, dadurch GEKENNZEICHNET, umfassend:
    das unter Druck stehende Fluidströmungssystem nach Anspruch 1; und
    Der Bohrer (90) weist einen oder mehrere Spülkanäle (92) auf, die über den Bohrer gebohrt sind und sich von den Kanälen (97) zur Vorderseite (99) des Bohrers (90) erstrecken, um das unter Druck stehende Fluid herauszulassen der Hammer.
EP17880617.0A 2016-12-12 2017-12-11 Druckfluidströmungssystem für einen dth-hammer und normalzirkulationshammer auf basis davon Active EP3553270B1 (de)

Applications Claiming Priority (2)

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US201615375286A 2016-12-12 2016-12-12
PCT/CL2017/050073 WO2018107304A1 (es) 2016-12-12 2017-12-11 Sistema de flujo de fluido presurizado para un martillo dth y martillo de circulacion normal basado en el mismo

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EP3553270A1 EP3553270A1 (de) 2019-10-16
EP3553270A4 EP3553270A4 (de) 2020-08-26
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CN (1) CN110382811B (de)
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EP3409878B1 (de) 2017-06-02 2021-08-18 Sandvik Intellectual Property AB Imlochbohrmaschine und verfahren zum bohren von gestein
EP3670823A1 (de) 2018-12-17 2020-06-24 Sandvik Mining and Construction Oy Bohrhammer-hammerbohrmeisselanordnung
EP3670824A1 (de) * 2018-12-17 2020-06-24 Sandvik Mining and Construction Oy Gesteinsbohrer zum schlagbohren
KR102271372B1 (ko) * 2020-03-31 2021-06-30 광성지엠(주) 제트 그라우팅이 가능한 천공 장치
KR102367844B1 (ko) * 2021-06-24 2022-02-25 광성지엠(주) 제트 그라우팅이 가능한 천공 장치

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CN110382811A (zh) 2019-10-25
MX2019006837A (es) 2019-08-26
CL2019001594A1 (es) 2019-10-18
EP3553270A4 (de) 2020-08-26
AU2017377092B2 (en) 2022-08-11
PE20191218A1 (es) 2019-09-11
CA3084682A1 (en) 2018-06-21
EP3553270A1 (de) 2019-10-16
AU2017377092A1 (en) 2019-07-04
WO2018107304A8 (es) 2019-02-21
CN110382811B (zh) 2021-11-02
KR102422904B1 (ko) 2022-07-21
WO2018107304A1 (es) 2018-06-21
ZA201903817B (en) 2022-01-26
KR20190104341A (ko) 2019-09-09

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