EP2781683A1 - Bohrmaschine zum Bohren beispielsweise von Erdboden- oder Felsformationen, und Verfahren zur Verwendung einer solchen Maschine - Google Patents

Bohrmaschine zum Bohren beispielsweise von Erdboden- oder Felsformationen, und Verfahren zur Verwendung einer solchen Maschine Download PDF

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Publication number
EP2781683A1
EP2781683A1 EP14157616.5A EP14157616A EP2781683A1 EP 2781683 A1 EP2781683 A1 EP 2781683A1 EP 14157616 A EP14157616 A EP 14157616A EP 2781683 A1 EP2781683 A1 EP 2781683A1
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EP
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Prior art keywords
axis
mast
arm
respect
machine
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EP14157616.5A
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English (en)
French (fr)
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EP2781683B1 (de
Inventor
Alessandro Ditillo
Stefano Massari
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Soilmec SpA
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Soilmec SpA
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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH DRILLING; MINING
    • E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B15/00—Supports for the drilling machine, e.g. derricks or masts
    • E21B15/04—Supports for the drilling machine, e.g. derricks or masts specially adapted for directional drilling, e.g. slant hole rigs

Definitions

  • the present invention regards a machine for drilling soils or rock formations of the type provided for example with a mast and an array of drilling rods, useable for example for positioning vertical or variously tilted tie elements.
  • the invention is particularly suitable to be applied to drilling devices which provide drillings of relatively small diameter, for example variable between 30 mm and 400 mm.
  • a machine body which bears the drilling means
  • clamps fixed to the base of the mast for gripping the drilling rods
  • an arm part of the main support of the mechanism for connecting the mast to the machine body.
  • the movement of the mast with respect to the machine body occurs through mechanisms of different types which are driven by suitable actuator means.
  • the various mechanisms may allow the machines to operate in various drilling configurations but they are generally optimised for maximising the performance only in some operations while having limitations in others. For example if optimised for vertical operations they shall be limited in other operations such as for example those for the execution of tilted tie elements wherein the drilling axis is tilted minimally with respect to the horizontal plane.
  • the second solution is not feasible in that with the arm resting on the horizontal plane and rotated by 90° around its longitudinal axis, the mechanism does not allow to control a vertical movement of the arm capable of increasing the tilting with respect to the soil and mounting it higher would lead to the aforementioned related transport problems.
  • the arm in the rotated condition described above is strained to bend laterally by the vertical loads. Such stress shall increase proportionally with the increase of the rotation angle and this angle might also need to be limited according to the lateral bending resistance of the arm.
  • the mechanism does not allow to rotate the arm up to moving the mast from the horizontal condition to the vertical condition, i.e. it does not allow to obtain the operating configuration C.3.
  • Such operating configuration C.3 can never be attained, not even starting from the operating condition C.1 because there is no joint with vertical axis capable of connecting the arm to the mast.
  • Another shortcoming of the mechanism lies in the fact that starting from the configuration C.1, it does not allow to attain the operating configuration C.2 given that there is no fulcrum with vertical rotation axis capable of connecting the arm to the machine body and at the same time there are no actuation means capable of allowing its swinging movement (as observable from Figure 2 which shows the mast positioned on the centreline plane).
  • Document DE20311847 shows in Figure 3 a machine provided with a mechanism (similar to the one illustrated for configuration C.3) which allows to laterally swing the arm reaching the operating configuration C.2 and it highlights the problems caused by the side overall dimensions of the clamps and the need to reduce the minimum distance "D" at which it is possible to move the drilling axis with respect to a wall when the tracks of the machine are parallel to such wall and the mast is vertical.
  • the mechanism does not have a joint with vertical axis between the arm and the mast like those indicated in fig 3 of the present application and it does not allow to reach the vertical operating condition C.3 with the mast rotated laterally by 90°.
  • An object of the present invention is to provide a machine and a drilling method capable of overcoming at least some of the previously outlined limitations and drawbacks of the currently known drilling machines.
  • such object is attained with a drilling machine having the characteristics according to claim 1.
  • such object is attained with a method for using a drilling machine having the characteristics according to claim 11.
  • such object is attained with a method for using a drilling machine having the characteristics according to claim 12.
  • such object is attained with a method for using a drilling machine having the characteristics according to claim 15. Further characteristics of the device are subject of the dependent claims.
  • FIG. 7-15 regard a drilling machine, indicated with an overall reference 100, according to a particular embodiment of the invention.
  • the drilling machine 100 may be arranged for drilling for example soil and/or rock formations, and it comprises:
  • the three proximal axes are two by two orthogonal to each other, and all three of them do not lie on the same plane; thus, regardless of the configuration of the arm 4, the mechanism subject of the present invention allows to rotate the arm with respect to two rotation axes 20, 22 perpendicular to each other and with respect to a third rotation axis 23 which is always perpendicular to at least one of the two previous axes 20, 22; for such purpose the first 20, the second 23 and the third proximal axis 22 may coincide with the actual and respective hinging pins 200, 230, 220 each of which makes only one degree of rotational freedom freely unconstrained, or can be simply ideal rotation axes ( Figure 13 , 15 ); in this second case the arm 4 may be fixed to the support mechanism 19 not with two distinctive hinging pins 220, 230 and the swingable support arm 21 -in such case substantially forming a cardanic joint- but for example with a ball joint;
  • the support mechanism 19 may for example be fixed through a pin 200, coaxial to the first proximal axis 20, to a flat and substantially vertical face suitably arranged at the front part of the machine body 15.
  • the rotatably unconstrained connection between the support mechanism 19 and relative front flat face of the machine body may be obtained for example through a bearing support, a bushing (both connected to the pin 200), guide slides or a center plate interposed between the machine body 15 and the centring surface 200A of the support mechanism 19 for the relative rotation.
  • the fixing between the parts is preferably with removable means, screws, bolts or pins.
  • the machine 100 is arranged for driving the support mechanism 19 allowing it to perform rotations ⁇ around the first proximal axis 20, substantially equal to or greater than 90° oriented in a single direction, more advantageously equal to or greater than 120° (for performing the corrections of the mast 1 on the vertical) and even more advantageously equal to or greater than 180° so as to allow the drilling from both sides of the machine.
  • the stroke end positions of the rotations ⁇ are preferably, even though not necessarily, symmetrical with respect to the vertical centreline plane -i.e. plane XZ- of the machine body 15.
  • the first proximal axis 20 is parallel to the front-rear direction of the machine 100, i.e. the direction of advancement thereof, for example the axis X of an ideal triad of Cartesian axes XYZ integral with the machine body ( Figure 7 ).
  • the proximal joint 103 is arranged for rotating the mechanical arm 4 even around the second proximal axis 23 -rotation ⁇ - and to the third proximal axis 22 -rotation ⁇ .
  • the mechanical arm 4 may be fixed to the machine body 15 through two hinges obtained for example on the swingable support arm 21 interposed between the two.
  • the first one comprises for example the proximal end of the arm 4, the swingable support arm 21 and the hinging pin 230 which connects them, the second hinge comprising for example the swingable support arm 21, the support mechanism 19 and the hinging pin 220 which connects them ( Figure 13A ).
  • the pins 230 and 220 are respectively coaxial to the axes 23, 22.
  • the machine 100 is preferably provided with at least two actuators 5 and 25A, also indicated as arm movement actuator 5 and first swinging actuator 25A, arranged for rotating the arm 4 respectively around the second proximal axis 23 and around the third proximal axis 22.
  • actuators 5 and 25A also indicated as arm movement actuator 5 and first swinging actuator 25A, arranged for rotating the arm 4 respectively around the second proximal axis 23 and around the third proximal axis 22.
  • the machine 100 is also provided with a second swinging actuator 25B, also arranged for rotating the arm 4 around the third proximal axis 22.
  • the first 25A and the second 25B proximal actuator are arranged on two opposite sides of the mechanical arm 4, preferably arranged adjacent to each other and to the arm 4; in other words, preferably the mechanical arm 4 and the first 25A and the second 25B proximal actuator are substantially coplanar.
  • the first 25A and the second 25B actuator may be fixed, at one end thereof, to the support mechanism 19, and at the other one to the arm 4.
  • the first 25A and the second proximal actuator 25B may be connected to the support mechanism 19 through a first coupling provided with a cardanic joint with two axes or a ball joint, and they are connected to the side of the arm 4 through a second coupling provided with a cardanic joint with two axes or a ball joint.
  • each cylinder 25A, 25B to accompany the movements of the arm 4, both when it rotates with respect to the axis 22 and when it rotates with respect to the axis 23, in that the cylinder is free to vary its tilting with respect to the arm without ever being stressed by bending loads.
  • the arm movement actuator 5 may be fixed for example at an end thereof to the arm 4, and at the other end to the swingable support arm 21.
  • the arm movement actuator 5 is fixed longitudinally to the arm 4 and along its lower side, in a position substantially symmetric with respect to the first 25A and to the second 25B swinging actuator, for example so as to be able to lift or lower the arm 4 with respect to a horizontal plane passing through the proximal axis 23.
  • the machine 100 is arranged for driving the distal joint 104 so as to rotate the drilling mast 1 with respect to the mechanical arm 4 by rotating around a first distal axis 9 integral with the slide 11 connected to the mast 1 or integral with the slide support 10 connected to the arm 4, preferably through at least a first distal actuator 26A -rotation ⁇ .
  • the distal joint 104 may be provided with a pin 90 coaxial to the axis 9 and which hinges the slide 11 to the slide support 10. Otherwise, analogously to the previous ones, it may be provided with bushings or center plates which allow the unconstraining of the rotation around that axis.
  • the machine 100 is arranged for driving the distal joint 104 and in particular the slide support 10 so as to rotate the drilling mast 1 with respect to the mechanical arm 4 also rotating around a second distal axis 3 (rotation ⁇ , still parallel to the axis 23) preferably through a second distal actuator 2, also indicated as tilting mast actuator.
  • the distal joint 104 may be provided with a pin 30 coaxial to the axis 3 and which hinges the slide support 10 to the arm 4.
  • the second distal actuator 2 may for example comprise a hydraulic cylinder fixed at an end to the arm 4 directly or returned through connecting rods 6.
  • the second distal axis 3 is preferably orthogonal or transverse to the first distal axis 9 and to the longitudinal axis of the mechanical arm 4.
  • the rotation axes 3, 9 of the distal joint may each be obtained with a relative hinging pin which allows a single degree of rotational freedom, or with cardanic joints, ball joints or other joints which allow each two or more degrees of rotational freedom.
  • the distal joint is also provided with a third distal actuator 26B also arranged for rotating the slide 11 -and thus also the drilling mast 1- with respect to the slide support 10 and thus to the mechanical arm 4 by rotating around the first distal axis 9.
  • Each of the actuators 26A, 26B advantageously comprises a hydraulic cylinder or other linear actuator arranged on the opposite side, with respect to the mast 1, in which the other distal linear actuator (respectively 26B, 26A) is located.
  • the arm movement actuator 5, the first 25A and the second tilting actuator 25B, the actuator for tilting the mast 2, the first 26A, the second 2, the third 26B and the fourth distal actuator 18 are or comprise hydraulic cylinders or other types of linear actuators, such as for example pneumatic cylinders, linear induction motors, rotary motors that actuate screw/nut screw systems.
  • the linear actuators are generally capable of developing considerable actuation forces, and thus considerable drive torques, while maintaining small overall dimensions which facilitate a better positioning thereof with respect to the rotation axes of the mechanism.
  • the linear actuators may advantageously have smaller dimensions and weights, for example with respect to rotary actuators; lower weight is an advantage particularly appreciated in the actuators located in the distal position: indeed, having lighter distal actuators 26A, 26B implies lesser cantilevered masses, and hence lower instability of the drilling machine 100 and greater lifting capacity of the mechanical arm. Due to the aforementioned reasons, i.e. the possibility of using suitable lever arms, the linear actuators are cheaper than the rotary ones considering the same developed torque. In addition, the linear actuators are almost free of clearances and thus they allow a greater precision in positioning the mechanism and they ensure the maintainment of the attained configuration even when the mechanism is subjected to external loads due to the work steps.
  • the use of said linear actuators to move the mechanism is thus advantageous with respect to the rotary actuators such as gear motors, which require the presence of a given angular clearance between the toothed wheels in order to ensure the correct gearing thereof.
  • said clearance increases as the number of reduction stages present in the rotary actuator increases.
  • part or all actuators 2, 5, 18, 25A, 25B, 26A, 26B may be replaced by one or more actuators each capable of actuating several degrees of freedom of the mast mechanism 102.
  • the support mechanism 19 may for example comprise a front plate 190 and a rear plate 192, both for example made of metal ( Figure 13A , 13B , 14 ).
  • the front rotation of the support mechanism 19 and, along with it, of the arm 4 by an angle ⁇ (gamma) with respect to the first proximal axis 20 is preferably actuated through at least one actuator 24A - conventionally also indicated as the first roll actuator 24A- which preferably, just like the second roll actuator 24B shall be described hereinafter, is a linear actuator.
  • the first roll actuator may be a hydraulic cylinder constrained (hinged) at a suitable point 240A to the machine body 15 and at another point 242A preferably hinged to the support mechanism 19 so that the extension and retraction of the stem 244A of the cylinder 24A applies to the support 19 a non-null moment and causes the rotation of the support.
  • Such rotation ⁇ (gamma) by at least 90° may preferably occur through a single continuous stroke of the cylinder 24A.
  • the at least one cylinder 24A may allow the support 19 to perform rotations greater than 90° with returns at several pitches, i.e. with several extension and retraction strokes of the stem 244A, by performing at least one second sequential actuation of the cylinder 24A once the external end of the stem 244A is disconnected so as to be reconnected in a different configuration.
  • actuator-fixing points 192A-192D are provided on the support mechanism 19 arranged to fix the support 19 to the actuator 24A.
  • Such fixing points 192A-192D are located preferably on the same circumference concentric to the first axis of proximal rotation 20 and spaced apart from each other by a given angle, so that a complete stroke of the cylinder 24 allows a partial rotation of the support mechanism 19.
  • suitable mechanical stop means for example a manually or automatically removable locking pin and disconnect the stem 244A of the cylinder 24 from the support 19, for example from the fixing point 192B.
  • the locking pin may for example be a pin inserted by hand into one of the pairs of holes 192A-192E so as to traverse at least one between the plate 192 and 190 and being engaged in a suitable abutment on the framework 15 so as to prevent the support mechanism 19 from rotating.
  • the peripheral sheets of the support 19, which connect the front plate 190 to the rear one 192, are obtained with a "cam" shape 32 so that when the stem 244A of the cylinder is disconnected it lies on the aforementioned sheets stopping after minimum rotation of the cylinder and relieving the operator from the need of holding the cylinder in a raised position; given that it weighs many tens of kilograms, this allows to facilitate the operation of disengaging the pins.
  • the cam shape 32 guides the head of the stem 244A up to positioning it at such point 192C and facilitating the insertion of the connection pin.
  • Said positioning of the roll actuators is advantageous in that it does not occupy space inside the machine body 15, simplifying the arrangement of the components contained in the machine body such as the thermal engine and the hydraulic circuit of the machine itself.
  • a first cylinder -e.g. 24A- operates in extension
  • the second one -e.g. 24B- operates retracting.
  • the blocking pin can be replaced with a linear actuator, preferably hydraulically controlled for the automatic unlocking and subsequent locking of the actuators 24A, 24B in the respective seats 192a, 192b, 242a, 242b, etc.
  • Such linear actuators are preferably remote-controlled.
  • the rotation ⁇ (gamma) of the support mechanism 19 may be actuated by at least one gear motor or any other equivalent rotary actuator.
  • a connection of the pinion sprocket type may be provided between the machine body 15 and the support 19 wherein the pinion of the gear motor is integral with the support mechanism 19 while the sprocket is integral with the machine body 15 or vice versa, so that the rotation of the pinion induces a relative rotation between the support mechanism 19 and the machine body 15.
  • the distal joint 104 may rotate the mast 1 around the first distal axis 9 thanks to actuators and mechanisms analogous to those described previously for rotating the support mechanism 19 around the first proximal axis 20.
  • an end of the first 26A and possibly the third distal actuator 26B which preferably, as mentioned, are hydraulic cylinders or other linear actuators, are fixed to the slide 11 on which the mast 1 is mounted so as to be able to slide longitudinally with respect to itself, and their other ends -for example the external heads of the relative stems- are fixed to a plate 33 integral with the slide support 10 so as to be able to apply, extending or retracting, an arm and a non-null moment with respect to the first distal axis 9.
  • the first 26A and possibly the third distal actuator 26B may cause the desired rotation stroke ⁇ (beta) of the mast 1 around the axis 9:
  • the stems of the hydraulic cylinder 26A, 26B will be allowed to perform another extension or contraction stroke, until completing the desired rotation ⁇ , which may thus be greater than 90° with respect to an initial condition wherein the drilling mast 1 belongs to a substantially vertical plane (plane X-Z with longitudinal axis of the mast parallel to Z) and a final condition in which the mast belongs to at least one substantially horizontal plane (plane X-Y with longitudinal axis of the mast parallel to Y).
  • the mast 1 and the arm 4 are substantially coplanar and the mast is rotated in a single direction around the axis 9 for rotations equal to at least 90°, or at least 180° or even 360° around the axis 9; - with one or more rotation strokes, in the latter case the actuators 26A, 26B being of the rotary type.
  • the mast mechanism 102 is arranged to allow the mast 1 to translate longitudinally on itself (arrow F1 in Figure 7 ) with respect to the arm 4 and in particular with respect to the slide 11 which is constrained to the arm through the slide support 10.
  • the mast 1 and the slide 11 may be fixed together for example through a prismatic coupling or any other suitable sliding guide, and preferably be actuated through a fourth distal actuator 18, also referred to as mast extraction actuator 18 ( Figure 7 ) which shall be connected at one of its end to the slide 11 and at the other end to the mast 1.
  • a fourth distal actuator 18 also referred to as mast extraction actuator 18 ( Figure 7 ) which shall be connected at one of its end to the slide 11 and at the other end to the mast 1.
  • the mast 1 is horizontal with respect to the soil and perpendicular with respect to the arm 4, the arm 4 is substantially parallel to the longitudinal axis X of the machine 100, it is not rotated with respect to the first proximal axis 20 and the drilling means are above the mast 1, i.e. the drilling axis is at a greater height with respect to the mast 1.
  • the mechanism 102 allows to use the at least one swinging cylinder 25A or 25B also for supporting the vertical loads and lifting the arm 4.
  • the loads acting in side action on the arm 4 -i.e. along the axis Z- may be at least partially counteracted by the cylinders 25A, 25B thus avoiding that it is the bending resistance of the arm 4 alone to counteract them and allowing a small dimensioning of the arm. From Figure 10 it can be observed that in this condition, by actuating the arm movement cylinder 5 so as to lift, according to the positive direction of the axis Z, the distal joint 104 of the arm 4, such joint is simultaneously moved in the positive direction of the transverse axis Y.
  • the mechanism subject of the present invention through a combined and suitably modulated actuation of the cylinders 5, 25A, 25B allows to obtain a movement (rotation) of the arm 4 on a vertical plane -for example XZ nullifying the movement components in the transverse direction Y.
  • the joint 104 is simultaneously moved in the negative direction of the axis Z.
  • the combined and suitably modulated actuation of the cylinders 5, 25A, 25B allows to obtain a movement in which the movement components nullify in the direction Z.
  • the obtained result is thus a side swinging of the arm 4 and the mast 1 on a plane X-Y maintaining the distal joint 104 at a constant height Z.
  • Such movement can also be independently obtained from the rotation angle ⁇ of the arm 4 with respect to the first proximal axis 20 and regardless of the value of the tilting angle ⁇ (phi) of the arm 4 with respect to the soil.
  • the third proximal axis 22 is parallel to the axis Y.
  • the mast 1 which was rotated by an angle ⁇ equal to 90° with respect to the plane longitudinal of the arm following the 90° rotation of the support mechanism 19 shall be tilted by an angle ⁇ (phi) with respect to the vertical.
  • the mast mechanism 102 allows to perform a further rotation ⁇ ' of the slide 11, and thus of the mast 1, with respect to the first distal axis 9.
  • This further rotation thus causes the overall value of the angle ⁇ to be greater than 90° and allows the returning of the mast 1 to the vertical position, thus allowing the machine 100 to reach the operating condition C.3 with the mast 1 vertical and rotated laterally by 90° with respect to the arm 4 as observable in figure 12 .
  • the vertical loads determined by the weights of the structures would tend to cause the rotation of the arm 4 and of the swingable support-arm 21 with respect to the third proximal axis 22 which is parallel to the transverse axis Y.
  • the aforementioned rotation is prevented by the support action (through push or pull) of the swinging cylinders 25A, 25B.
  • the cylinder 5 may however be actuated and in such case it only serves the function of positioning the arm 4, thus allowing the swinging rotation of the arm 4 around the second proximal axis 23 and only having to overcome the frictions of such rotation.
  • the same arm movement cylinder 5, which in the operating configuration of figure 7 serves the function of lifting the arm 4 may also serve a main function of the swinging movement of the arm 4 when the machine 100 is in the configuration of figures 11 or 12 .
  • the swinging actuators 25A, 25B which in the operating configuration of figure 7 serve a function of swinging the arm 4, to also serve a function of lifting the arm when the machine 100 is in the configuration of figure 11 or 12 .
  • the mechanism 102 allows the tilting of the arm 4 with respect to the soil with an angle ⁇ (phi) which may also be negative, so as to move the mast 1 and the drilling means 12 to the lowest height possible with the aim of lowering the barycentre and improving the stability of the machine.
  • ⁇ phi
  • Such rotation can be obtained through the second distal cylinder 2 and it allows the moving of the first distal axis 9 to a horizontal position.
  • the mechanism 102 allows to reach all the operating configurations 1,2,3,4,5 and 6 with only one machine for small diameter drilling operations, overcoming the shortcoming of the mechanisms of the known art and allowing to maximise the performances under all work conditions.
  • the mechanism 102 upon reaching the operating condition C.5 visible in figure 10 , allows to tilt the mast 1 with tilting ⁇ greater than the maximum ones allowed by the known mechanisms when the mast is arranged for operations with tie elements with transverse drilling. In particular this tilting may be increased so as to move the mast 1 from a horizontal position to a vertical position with respect to the soil and this may be carried out regardless of the tilting ⁇ (phi) of the arm 4 with respect to the soil.
  • FIG 12 which is a view from B of figure 11 , it may be observed that the attained configuration allows to perform vertical drilling operations and simultaneously having an orientation of the clamps 13 such to generate the least overall dimensions possible in the Y direction with respect to the drilling axis.
  • Such configuration can be obtained both with the arm 4 arranged with its longitudinal axis on a horizontal plane and with arm 4 tilted by a non-null angle ⁇ (phi) with respect to the horizontal, and in addition it can be obtained with a small side cantilever of the drilling axis AT with respect to the machine. This is particularly advantageous when performing a series of aligned drilling operations with respect to a wall and as close as possible thereto, this application being typical of consolidating buildings.
  • the mechanism 102 indeed allows to move the drilling axis AT very close to the wall and simultaneously having tracks oriented parallel to the wall. This allows to make the performance of the series of drilling operations faster in that once one drilling operation is completed, it is sufficient a simple translation of the machine to move to the point provided for the execution of the subsequent drilling.
  • the transverse positioning of the drilling axis AT in the Y direction may be corrected when the arm 4 is rotated by 90° around its longitudinal axis, i.e. upon executing a 90° rotation with respect to the first proximal axis 20 activating the arm movement actuator 5 which will perform a function of swinging the arm 4 in this configuration.
  • This will allow the moving of the drilling axis AT slightly inwards with respect to the position of the tracks 27A, 27B so that the clamps 13 are flush with the outer wall of the tracks.
  • the mechanism 102 may allow to reach the operating condition C.3 with the vertical mast 1 rotated by 90° with respect to the arm 4 and arranged towards the left track 27A of the machine or with the vertical mast 1 rotated by 90° with respect to the arm 4 and arranged towards the right track 27B of the machine.
  • the front rotation performed by at least one rotation actuator for example a cylinder 24A, 24B or a gear motor with pinion
  • the front rotation should be by at least 90°.
  • the mechanism 102 may reach the operating condition C.3 or the operating condition of Figure 7 starting for example from a transport condition shown in Figure 16, 16A , wherein:
EP14157616.5A 2013-03-11 2014-03-04 Bohrmaschine zum Bohren beispielsweise von Erdboden- oder Felsformationen, und Verfahren zur Verwendung einer solchen Maschine Active EP2781683B1 (de)

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IT000360A ITMI20130360A1 (it) 2013-03-11 2013-03-11 Macchina da perforazione per perforare per esempio terreni e/o formazioni rocciose

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EP2781683A1 true EP2781683A1 (de) 2014-09-24
EP2781683B1 EP2781683B1 (de) 2019-11-06

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109838209A (zh) * 2019-03-29 2019-06-04 成都哈迈岩土钻掘设备厂 一种多角度定向勘探管棚钻机
IT201800004757A1 (it) * 2018-04-20 2019-10-20 Supporto articolato di dispositivo mast per una perforatrice e relativa perforatrice
CN111594045A (zh) * 2020-04-13 2020-08-28 中北大学 一种支座旋转式隧道钻孔设备
IT201900005026A1 (it) * 2019-04-03 2020-10-03 Comacchio S R L Macchina perforatrice articolata compatta, per perforazioni in ambienti aperti ma anche e particolarmente per scavi e perforazioni in spazi angusti, gallerie e/o cunicoli
CN114183083A (zh) * 2021-12-14 2022-03-15 安徽理工大学 一种模块式钻杆自动运移装置
US20230022559A1 (en) * 2021-07-22 2023-01-26 Christopher Tyler King Adjustable Drilling Rig

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EP0016717A1 (de) * 1979-03-26 1980-10-01 Etablissements Montabert Gelenk-Stützarm für Bohrlafette
DE20311847U1 (de) 2003-07-31 2003-10-02 Klemm Bohrtechnik Zweigniederl Bohrvorrichtung
DE20314277U1 (de) * 2003-09-12 2003-12-18 Hütte Bohrtechnik GmbH Bohrgerät zum Bohren von Löchern im Erdreich
EP1696100A1 (de) 2005-01-24 2006-08-30 Comacchio USA Corp. Drehbarer Träger für einen neigbaren Bohrmast
WO2006096110A1 (en) * 2005-03-11 2006-09-14 Atlas Copco Rock Drills Ab Rotation device for a boom of a mining or constructions work rig, rig and boom
DE102007012055A1 (de) 2007-03-13 2008-09-18 Klemm Bohrtechnik Zweigniederlassung Der Bauer Maschinen Gmbh Bohrgerät, insbesondere zum Erd- und Gesteinsbohren
WO2009138556A1 (en) * 2008-05-12 2009-11-19 Sandvik Mining And Construction Oy Rotating device

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Publication number Priority date Publication date Assignee Title
GB2028693A (en) * 1978-08-26 1980-03-12 Grimshaw G Mining drill boom
EP0016717A1 (de) * 1979-03-26 1980-10-01 Etablissements Montabert Gelenk-Stützarm für Bohrlafette
DE20311847U1 (de) 2003-07-31 2003-10-02 Klemm Bohrtechnik Zweigniederl Bohrvorrichtung
DE20314277U1 (de) * 2003-09-12 2003-12-18 Hütte Bohrtechnik GmbH Bohrgerät zum Bohren von Löchern im Erdreich
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Cited By (11)

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Publication number Priority date Publication date Assignee Title
IT201800004757A1 (it) * 2018-04-20 2019-10-20 Supporto articolato di dispositivo mast per una perforatrice e relativa perforatrice
WO2019202549A1 (en) * 2018-04-20 2019-10-24 Beretta Alfredo S.R.L. Articulated support for a drilling mast of a drilling machine and related drilling machine
US11280138B2 (en) 2018-04-20 2022-03-22 Beretta Alfredo S.R.L. Articulated support for a drilling mast of a drilling machine and related drilling machine
CN109838209A (zh) * 2019-03-29 2019-06-04 成都哈迈岩土钻掘设备厂 一种多角度定向勘探管棚钻机
IT201900005026A1 (it) * 2019-04-03 2020-10-03 Comacchio S R L Macchina perforatrice articolata compatta, per perforazioni in ambienti aperti ma anche e particolarmente per scavi e perforazioni in spazi angusti, gallerie e/o cunicoli
EP3719247A1 (de) * 2019-04-03 2020-10-07 Comacchio S.r.l. Kompakte gelenkbohrmaschine, geeignet für aussenbohrungen sowie auch und insbesondere für aushub und perforation in engen räumen, galerien und/oder durchgängen
CN111594045A (zh) * 2020-04-13 2020-08-28 中北大学 一种支座旋转式隧道钻孔设备
CN111594045B (zh) * 2020-04-13 2023-09-26 中北大学 一种支座旋转式隧道钻孔设备
US20230022559A1 (en) * 2021-07-22 2023-01-26 Christopher Tyler King Adjustable Drilling Rig
CN114183083A (zh) * 2021-12-14 2022-03-15 安徽理工大学 一种模块式钻杆自动运移装置
CN114183083B (zh) * 2021-12-14 2023-11-28 安徽理工大学 一种模块式钻杆自动运移装置

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