DE1900210A1 - Rotary drilling jig - Google Patents

Description

HUGHES TOOL COMPANY, Houston, State of Texas (V.St.A.)

Rotary drilling jig

The present invention is in the field of rotary drilling apparatus and is particularly used herein in use on light, easily transportable rotary or rotary drilling devices described which are used for drilling relatively small boreholes, for example up to a maximum Drilling depth of about 15 i &> are particularly suitable. Such boreholes can have different diameters, namely between 7 »5 or 10 cm for test bores up to 1.50 m or more for large drills for which the invention will be described below.

The invention particularly relates to a rotary drilling device having an angle to the ground

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held drill pipe, one at its lower end attached drilling tool, further with a rotary drive for rotating the drill string and the drilling tool and with a thrust drive, which presses or pushes the rotating drilling tool into the ground via the drill rods. drives in. The thrust acts axially on the drill rod or the drive rod, either in bursts or continuously.

Various devices are known to the thrust · and torsional forces on the drill pipe and the Transfer drill string. While more and more hydraulic drives to apply the axial »and rotational forces were used, their coupling with the drill pipe was almost exclusively done by mechanical components, e.g. turntables, shafts, gears, chains, sprockets, ropes, etc. Such mechanical couplings have several disadvantages, not the least of which is the cost of these couplings and their brackets and ancillary equipment such as an auxiliary linkage, housings, winch motors, and the like. In addition, these arrangements result in considerable Schwiagungs phenomena, friction losses and appropriate wear and tear, which appropriate lubrication, monitoring, additional maintenance and inevitable and require expensive replacements of individual parts. 909885/0224

Another disadvantage of known devices of this type is the difficulty in actuating and controlling them. When using mechanical clutches, the control device often has rigid, manually operated clutches and slides. When using hydraulic drive units, a separate valve was usually provided for each drive unit, this valve generally during a full cycle of operation (ie starting with the drilling tool being placed on the ground, lifting it, throwing off accumulated cuttings, lowering it back to the ground and simultaneously applying a rotary and thrust force until the drilling tool again must be raised) must be opened and closed several times. The entire control system in known devices of this type is generally a combination of a multiple (

number of mechanical devices and hydraulic valves that are so numerous and so many manipulations require that they occupy the attention of the operator to a large extent in order to operate them and therefore distract from observing the drilling tool and its advance in the borehole. aside from that the known controls have the disadvantage of additional costs, high maintenance costs and a high probability of being actuated incorrectly

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Control functions, especially when the Operator is relatively inexperienced.

These and other disadvantages are intended to be eliminated by the invention. For this purpose, starting from a rotary drilling device with a drill pipe held at an angle to the ground, a drilling tool attached to its lower end, furthermore with a rotary drive for rotating the drill string and the drilling tool and with a linear drive, which is pushes or drives rotating drilling tool into the ground via the drill rods, proposed according to the invention, that the rotary drive is a motor directly coupled to the drill string; and that the drill pipe at least has a non-circular cross-section over part of its length and at least the motor shaft designed as a hollow shaft has an axial opening with a correspondingly non-circular cross-section over part of its length, in which the non-circular part of the drill rod is form-fitting and slides axially under the influence of the thrust drive is led. The thrust drive is also coupled directly to the drill pipe; from the axial opening in The drive rod or the drill rod extends after the al3 hollow shaft up into a bore in a hydraulic pressure cylinder and ends in a direct connection with the

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Piston of this cylinder arrangement, so that when pressure is applied to the upper piston surface, the bridge is applied is transferred directly to the drilling tool via the driver rod.

Another essential feature of the present invention is the combination of two or more hydraulic power units or drive units, in particular the rotary drive and the thrust drive designed as a pressure cylinder arrangement with a special simple hydraulic control system. This system can either be used with or without the direct above Find power transmission use. Preferably two valves are used, one for rapid Moving the cylinder that applies the thrust and the other to operate the rotary motor. The hydraulic lines of these two valves are connected so that no pressure medium flows to the engine or its valve when the valve for the The thrust actuator is actuated and the pressure medium passes through the thrust cylinder, while when the valve is for the thrust drive is in the neutral position, the flow of pressure medium to the thrust cylinder is blocked and all of the pressure medium to the valve controlling the engine is blocked flows. This measure makes it possible to leave the ßotary valve open most of the time, so that during

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During the drilling process, only the fast valve for the linear actuator needs to be operated. When using a Auger drill bits allow the same valves to lift the drill bit and remove the cuttings simply by actuating them of the valve assigned to the thrust actuator.

According to a further embodiment of the invention, a controlled pressure relief valve is switched on in those pressure medium lines which connect the cylinder of the thrust actuator with a slow valve for the thrust actuator, the latter generating the thrust force when the rotating drilling tool arrives on the ground. This pressure relief valve measures the pressure on the pressurized side of the cylinder forming the thrust actuator, and when this pressure has reached a certain working pressure, the pressure relief valve is actuated and lets the penetrating fluid out into the tank line. A valve provided in the inflow control valve maintains the pressurized fluid in the cylinder and can also serve to drain the fluid when the slow valve is actuated for the linear actuator in the reverse direction "to the drill bit to lift.

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In the following, the invention is explained in more detail using an exemplary embodiment shown in the drawing. In the drawing shows:

1 is an overall perspective view

raised to the working position at the rear of a truck frame Drilling device, the truck frame the hydraulic pumps that Internal combustion engine, the tanks for the hydraulic fluid and carries the fuel and all other auxiliary equipment; the drill pipe and the drill are raised in one Position shown in which the drill is just above the surface of the earth;

Fig. 2 and 3 show longitudinal sections through the

Drilling string & arrangement of the drilling device, which is intended here in particular for vertical drilling, although they also outside the vertical using one or both of their assigned Swivel cylinder can be operated; of this arrangement, Fig. 2 shows the lower one and Fig. 3 shows the upper one Part of the drill string assembly;

Fig. 4- is a schematic view of the hydraulic circuit as well as all devices controlled by these;

Fig. 4A is an enlarged schematic view of one of the control valves shown in Fig. 4-; and

Fig. 5 is a schematic representation of the automatic Control system for the slow hydraulic thrust actuator.

The overall device shown in Fig. 1 comprises the Bohraast or drill string 10, the truck 11, the fuel

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engine 12, the pump arrangement or triple pump 13, the tank 14 for the hydraulic fluid and a pair of winches 16H and 1 €> L, with which the frame 17 c.es truck can be raised to stabilize the drilling device, as well as the auxiliary equipment and the drilling load, which advantageously should not rest on the springs of the truck 11. Furthermore, a hydraulic cylinder 18 and its piston rod 19 can be seen in Fig. 1, by means of which the haste or Strand 10 between its working and transport position; can be moved. In the transport position the mast 10 is supported by a bracket 21. The drilling mast 10 can be pivoted on fork-shaped bearing bars 22 stored and can by means of a hydraulic swivel cylinder 23 together with the bearing bars to the side be tilted so that the drilling axis can also be relocated outside of the 7ertikelen. The operator is marked with 0 and their working seat with S.

The main parts of the load assembly 10 are also shown in FIG Fig. 1 can be seen; this includes, in particular, the hydraulic motor 50, the drill rods or the pick-up rods 60, the rod attached to the lower end of the driver Drilling tool 70 and the thrust cylinder 80. On the back of the carrier vehicle are two lengthways arranged slide rails provided which

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on a bearing 15 built into the vehicle frame 17 are supported, and a vag 29 is between a front (transport position and that in the drawing rearward working position shown movably arranged on the slide rails. The bearing 15 acts as a turntable and can be rotated by 240 ° about an axis lying on the longitudinal axis of the vehicle frame. the The bearing is actuated by means of a pair of hydraulic cylinders, not shown, which run parallel to the Is arranged longitudinal axis of the vehicle and hinged to the vehicle frame. The free ends 58 of these Pistons belonging to cylinders are connected via a chain 57 to a piston connected to the underside of the bearing 15 Chain wheel 56 connected (see Fig. 4) · The chain wheel 56 and chain 57 are schematic in the hydraulic circuit diagram indicated in accordance with FIG. The carriage 29 carries the storage holae 22 and all of them to the mast arrangement 10 appropriate ropes as well as all auxiliary equipment, such as the main drive motor 12, the triple pump 13 and the tank 14 for the hydraulic fluid. The slide 29 can be moved by means of a hydraulically operated single cylinder 25 (FIG. 4) which is mounted on the turntable 15 is arranged between the rails 20, can be pushed back and forth.

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Vie in Figs. 2 and 3 can be seen, this is on The most downwardly extending organ is the drill rod or the driver rod 60. You driver st eye 60 has non-circular and in the illustrated embodiment, square cross-section; however, they may have any other suitable cross-sectional training that requires

_ allows that they are in the hollow shaft 51 of the rotary motor 50 is form-fitting, this version must allow an axial sliding movement in.der motor shaft. In practice, only that part of the hitch rod that is slidably mounted in the hotor shaft is needed, have a non-circular cross-section. The lowest As can be seen in FIG. 2, part 61 of the drill rod 60 has an opening 62 running in the transverse direction in which a through correspondingly aligned openings in a hollow shaft 71 of the drilling tool 70

P through pin 63 is fitted. Part 61

can have the usual round cross-section; however, a non-circular cross-section is to be preferred for better transmission of torsional force to the drilling tool. The same goes for the top dogging> cane, is that switches the thrust cylinder 80 back and forth, but does not enter the Hotorwelle 51st The shaft 71 of the drilling tool has an inner pocket, not shown, in which the lower end of the drill rod 60 is held in such a way that when a

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Thrust the power transmission via the shaft itself and not via the pin 63.

If the drill rods in FIGS. 1 to 3 are followed, starting from its lower end, the following arrangement results. The drill rod 60 is initially through a shock absorbing spring 26 performed below of the engine is attached. Behind the spring 26 follows a convolution 27 "which leakage currents in the longitudinal direction of the to prevent mtnehaerstange and at the lower end of the motor shaft 51, with this and the driving rod ait rotating, is connected. By fastening the packing arrangement 27 to the rotor shaft 51, it is achieved that the latter takes part in the longitudinal movements of the driver rod 60. From there is the drive rod or the drill pipe 60 passed axially through the entire shaft 51 and extends through the upper End 53 of the motor shaft and through the fixed connection component or the drilling mast base 30 and through the open lower end 81 of the thrust cylinder 80 in its interior. The driver rod 60 is in the thrust cylinder 80 guided upwards and ends in a round end component 66 which is screwed into a pair of locking nuts 84 arranged in the piston 83. Shortly below the threaded end 66, the drive rod has a region 67 that is round in cross section with an intermediate

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diameter which is inserted inside the laying body of a tapered roller bearing 85. The outer bearing shell of the layer 85 is a press fit in the bore of a bit cup-shaped component 86 of the piston. The order, consisting of the trailer bar, the bearing and the Lock nuts 84 are against pulling out of the piston in Abwirtarlohtung by means of a split Retaining rings 87 "of the bearing 85 arranged below the outer bearing shell and in an annular groove in the The bore of the cup-shaped component 86 is engaged, secured. Another cup-shaped component 88, which is inserted into the bore of component 86 is inserted, its annular band 89 on the upper end face of the outer bearing shell of the bearing rests, while the base 90 of the cup-shaped Component 88 is arranged between the upper end 66 of the follower rod 60 and the base 91 of the piston component 86. A pair of adjusting screws 92 and 93 are in the inclined opening screwed into the base 91, namely in such a way that the under «adjusting screw 92 abuts against the base 90 of the cup-shaped component 88 and thereby pushes the band 89 against the bearing 85 to the bearing and the holding length "wipe the" pot-open component 88 and the retaining ring 87 to clamp "Suitable you" Tunge and bearing rings are between the outer circumference of the

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Piston 83 and the inner wall of cylinder 82, as shown, is provided.

The thrust cylinder 80 is open at its lower end because it is relatively difficult to achieve a tight passage for the polygonal rotating drill pipe to provide 60; the cylinder sleeve is 82 for the same reason provided at its lower end with an external thread, which is provided in the base component 30 in the upper find one Longitudinal opening 31 engages existing threads. Bas the upper end 53 of the hollow shaft of the motor 50 is surrounded by a pack 32 which is in the opening of the base component 30 of the mast sits. In this way there is the drive rod between the rotary motor and the thrust cylinder extremely little cause for leaks from which the hydraulic fluid can flow out. Of course, the base component 30 ensures a fixed holder for the thrust cylinder 80. Such a holder could also be produced in other ways the lower end 81 of the cylinder with a component, e.g. a shaft stub 53 » which would rotate with the drill pipe 60 but would be fixed with respect to the end 81, to allow relative sliding movement of the drill string. In addition, packs would have to be used that contain one Leakage current between the round outer wall of this

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additional component and the end 81 of the cylinder would have to prevent.

The thrust cylinder 80 has a tight and internally threaded top cap 95 on which a with Threaded connection piece 96 for a hydraulic line F and a connecting channel 97 to the passage of the pressure medium to and from the upper end of the thrust cylinder above the piston 83 are arranged. A similar connection piece 36 and a connecting channel 37 for the pressure medium which is supplied to the lower end of the thrust cylinder 80 below the piston 83 provided on or in the base component 30.

As already indicated above, the drive rod 60 can alternatively be connected to the piston * 83 in such a way that the two components both rotate together and move axially as a unit. This modified embodiment makes it possible to dispense with a mechanical coupling formed by the bearing 85, whereby all other components belonging to the piston with the exception of the piston body 86 can be omitted and the body 86, apart from a longitudinal opening for the upper end of the driver rod _t can be designed as a solid body. In the last-mentioned embodiment, the

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drive rod and the piston through a screw connection ο «the like. be merged. The problem the leakage losses between the piston and the cylinder wall would, however, be more noticeable, however, could largely be eliminated by using a reasonable number of suitable rotary seals.

As a holder for the push cylinder 80 in addition to the base component 50 of the drilling mast, the push cylinder 80 is encompassed and supported by a support device 58. This support device 58 has one outward directed base flange 41 and an annular head part 42 serving as a holder for a pack, wherein the flange 41 with the head part 42 through over the Perimeter spaced-apart hip 46 is connected. The head part 42 is provided with an external thread, which engages in a thread in a cap 43, via which a Ατ1 aidruck on the packing ring 44 and the fiingpackungen 45 can be exercised, which between the head part 42 and the cylinder jacket 82 are arranged. When an axial pressure is applied to the hanging seals 45, they are pressed apart radially and nestle closely against the radially delimiting components 42 and 82. The packing rings 45 do not serve to prevent leakage flows of the pressure medium, son-909885/0224

that should primarily stabilize the mast arrangement in such a way that that an angling of the cylinder at its contact point with the head part 42 of the support device 38 Is avoided.

The support device 38 is with its splash at 39 with welded to base component 30 of the drilling mast, and base component 30 is in turn at 40 to bearings 28 the spars 22 welded. In this way, the bearing bars 22 support the entire drill mast assembly 10. A row circumferentially spaced bolts 33 pass through flange 34 of the base member 30 screwed and hold the motor 50 in its intended Position with its shaft aligned coaxially with the thrust cylinder 80.

The hydraulic motor 50 (this can be driven by an electric motor, a pneumatically operated motor or the like «to be replaced) is only indicated in the drawing because the present invention does not relate to the drive motor itself. Suffice it to say here that a hotary motor used here has a high torque under load over a rotational speed range of should develop around 150 to 5 revolutions per minute or to a standstill (overload torque). the The motor shaft must have a sufficiently large cross-section

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sit so that it can be provided with an axial opening into which a driving rod non-circular cross-section can be used axially sliding, as proposed by the present invention. A special one Hydraulic motor that has already been used successfully in conjunction with the measures taken by the invention is the vane motor MHT-250 from Vickers Incorporated. This motor has the following characteristics:

Torque: 620 kpm at 140 at pressure drop across the motor in one speed range from 5 to 150 o / min

Efficiency: 88 to 92 % at 105 - 140 at, 83% at 10 rpm and 105 at

Displacement: 0.0031 vaP per revolution

Fluid consumption: maximum 474 liters per minute

at 150 rpm

Weight without shaft: 200 kg

Dimensions: 39.5 cm diameter

29.5 cm axial length of the case

The functioning and the control of the new device are based on the hydraulic shown in FIGS. 4 and 4A Circuit diagrams explained below. As can be seen in Figure 4, these are the most essential parts the hydraulic system of the pressure medium tanks or! thanks

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, pumps 13a, 13b and 13c, which are actually sections of the triple pump 13 provided with a single shaft, the valve group 102 and its associated Supply line 103 and the tank return line 104, the valve group 106 and their supply line 107, the last-mentioned valve group also being connected to the return line 104, and a foot valve 109. The valve group 102 includes valves 111, 112 and 113 which are used to control the im Rapid traverse operated devices of the system or of the thrust cylinder 80 (in rapid traverse) of the rotary motor 50 and the winch motor 75 serve. Valves 121 to 129 belong to group 106, which control the slower working, Control devices loaded with a smaller amount of pressure medium per unit of time, i.e. the side pivot cylinder 23, the position cylinders 24L and 24R, the cylinder 18, the push cylinder 80 (with slow Gear), cylinder 25, winch cylinders 16L and 16R and cylinders 76 and 77 · It should be noted that the push cylinder do for fluid admission is connected to both the rapid traverse valve 111 and the slow traverse valve 124, the rapid traverse to the Moving the boring tool in or out of the borehole or out of the borehole is used during slow travel for drilling itself and for applying the thrust load is used. Usually just one is the

Valves 111 and 124 actuated but are not locking devices provided that prevent simultaneous closing, as this does not cause any particular damage can arise. The slow speed valve becomes more normal » operated intermittently or in bursts, the operation in the downward drilling position (crossed arrows) for a few seconds followed by a return to the neutral position shown Positions to create even pressure until the drilling tool starts drilling down and reduce the pressure on the piston.

The other valves and the ax Langeamgang valve assembly 106 associated switching elements are substantially conventional design. A special hydraulic reservoir line 108 is provided for adjusting the turntable cylinders 24L and 2411 and pressurizes them with pressurized oil. The operation of these two cylinders is unusual to a certain extent, as indicated by the symbolically represented chain wheel 56 and the chain 57 which runs around the chain wheel and is connected at both ends to the piston rods 58 of the cylinders 24L and 24R. For example, if the piston of cylinder 24L is moved to the right to rotate sprocket 56, and hence rotating disk 15, counterclockwise, the piston of other cylinder 24B must necessarily

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moved to the left. With regard to the control of the pressure medium flow, this means that when pressure medium is applied the piston rod side of the cylinder 24L via line 144 to the piston rod side of the cylinder 24R must be relieved via the line 146, so that the two piston rod sides via a customary

^ guided hydraulic valve 122 suitably connected to one another are. The two lines 144 and 146 are passed through the double equalization valve I3I, which prevents the fluid from being drained from one cylinder until the other is pressurized, so that the otherwise loose side of the chain 57 is kept taut. The adjustable quantity control valves measure the passage amount of the hydraulic medium to and from the piston rod sides of the cylinders 24L and 24R control the operating speed of these cylinders

P and thereby the speed of rotation of the turntable in to keep appropriate limits.

While the turntable 15 from the piston of the cylinder 24L and 24R is rotated counterclockwise, the hydraulic fluid must of course be from the piston rod side of the cylinder 24L and flow into the piston rod side of the cylinder 24R. The biggest Part of the hydraulic medium is

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connecting line 59 between the piston tops of the cylinders during successive movements in opposite directions Sightings back and forth, with the direct connection of this line to the hydraulic fluid tank 14 via line 108 ensures that pressure medium losses balanced and the piston sides of the cylinders are always filled with pressure medium «

It should also be mentioned that the low speed valve 124 · is the only valve of valve group 106 which is practically continuously operated. When digging of any kind of the borehole are the stabilizer cylinders 16L and 16R only actuated at the beginning and at the end of the drilling process; the same also applies to the lifting cylinder 18, the sliding cylinder 25, the turntable cylinders 24-L and 24JEt and possibly also for the side angle cylinder 25 · Die Cylinders 76 and 77 are only used sporadically.

Various others in the hydraulic circuit diagram according to Fig. 4 Elements shown, such as the test valves 135, the pressure shock absorbers (Orifice plate-like devices) 134-, the pressure gauges 136, the pressure relief valves 137 and the filter 138, are of well-known design, the filters largely as protection for the drive components, such as the motor 50 are provided. The engine 50 is equipped with a special drain line 139 which

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between the motor housing and the tank 14 is connected to that formed by leakage currents over the motor blades Discharge hydraulic fluid and thereby protect the seals from pressure build-up. The control valve 141 has the task of ensuring that the motor housing is constantly filled with the hydraulic fluid for lubrication purposes

With regard to the supply lines and the pumps, it should be noted that the hydraulic fluid supply for all three Pump sections via a common line 142 and a filter 138 (200 mesh) in the tank 14 takes place. That Filter 138 is connected to the pump section via branch line 142c 13c, the branch line 142b with the pump section 13b and the branch line 142a with the pump section 13a connected. The tank 14 is also provided with an externally readable level indicator and with a Temperature measuring device 143 equipped.

The pump section 13c, the delivery rate of which is 220 l per minute, is directly above the supply lines sweig 103a connected to the collecting line 103, while the pump section 13b, whose delivery rate 246 1 per Minute, is initially connected to the valve 109 actuated by the foot pedal. The valve 109 is normally only when pulling out the loaded drilling

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tools 70 from the borehole, and used during the throwing off of the cuttings when a high speed is to be achieved by parallel switching of the two pump sections, which subjects the cuttings lying on the drill passages to high centrifugal forces and ejects them from the borehole, and is finally used when the cleared drilling tool is lowered to the bottom of the borehole.

An essential feature of the invention is the switching of the overdrive valve 111 and its connections both to the thrust cylinder 80 and to the supply line 103 »which leads to valve 112 of rotary motor 50. In the drawing these valves are in their neutral positions shown; if the pump is actuated, the hydraulic medium is supplied via the supply line 103 put into circulation and via the return line 104 returned to tank 14 since winch valve 113 is also in its neutral position. (Sa the Winch 75 is only operated in special cases, it will not be discussed in detail here.) Venn the valve body or slide 114 of the valve 111 (see Fig. 4A) within the housing 115 of the valve is moved to the right to its forward (down) operating position, the hydraulic fluid flows through the branch 116 of the supply line 103, through the valve 111

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according to the arrow pointing upwards and through, the line 117 to the piston top of the Sehubzylinders 80. At the same time, a reflux circuit is established from the piston rod side of cylinder 80 via line 118 and formed downwards by the valve 111 to the return line 104 (as is symbolically indicated by the arrow pointing downwards). Furthermore, the forward movement of the valve body 114 simultaneously causes the Main flow line 103 is blocked, as by the broken line or the gap 119 between the Arrows is shown symbolically. This prevents any flow of the hydraulic oil up to the rotary motor 50 via its valve 112 and ensures that all hydraulic fluid flow for the rapid movement of the tow bar 60 and the drilling tool 70, which are directly connected to the piston of the thrust cylinder 80, is used.

Assuming that the drilling tool is fully withdrawn to a position above a borehole to be excavated, both valves 111 and 112 can be in their Forward directions (right in the figures) are switched simultaneously. The valve 112 has a detent 120 «Of which can be used to hold it in its forward position so that the operator can Valve 112 can be disregarded until the wellbore

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is driven to the desired depth. The fluids Supply via valve 111 to thrust cylinder 80 quickly lowers the drilling tool to the bottom of the borehole, and the only action to be performed by the operator thereafter is that of the valve body 114 to release connected handle 150 · As the valve body in its neutral position at both ends, as symbolically represented by the spring symbols 135, is biased by springs, it will return to the neutral position when the handle 130 is released. Thereupon the hydraulic fluid flow through the valve 111 and the thrust cylinder 80 are immediately blocked and diverted to valve 112 and to motor 50 - as a result alone the release of a single valve control device.

Since the forward position of the valve body is assigned to 114 of the valve 112 of the rotary movement of the drill tool during penetration into the ground, this operation is performed automatically, and the operator is necessary slows down by adjusting dee valve body of the Langeamgang valve 124 operate between the forward "and Neutral positions · This control activity is the only activity that the operator has to carry out during the entire drilling process.

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Reference is now made to 71g x 5 of the drawing. The development shown in Fig. 5 relates to a pilot operated drain valve 147 and a control valve 146 which is connected to that part of the hydraulic circuit which comprises the hydraulic lines 117 and 118 which connect the thrust cylinder 80 and its high-speed and low-speed valves 111 and 124 '. (The last-mentioned valve differs from valve 124 according to FIG. 4 only in that the valve 124 has a detent 140 which holds the valve in the forward position, wherein line 11? connected to the supply line 107 and the line 118 to the tank line 104 ·) You valves 14-7 and 148 thereby contribute to the simplification the control that the Langsangang valve 124 * Moved to its forward or first position during the drilling process (rapid traverse valve 111 in the neutral position shown in the drawing) and held there to compensate for the drilling process. Without these valves 14-7 and 146, the operator must have the Thrust by intermittent actuation of the long • amgang valve 124- to the forward position and back Apply to the drilling tool for the neutral position shown.

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The (automatic) operating sequence of valves 147 and 148 did as follows: After adjusting valve 124 * The hydraulic medium flows over into its forward position, symbolically represented by the crossed arrows this valve, the line 117 and through the control valve 148 to the piston top of the thrust cylinder 80. Due to the resistance from the ground to the drill, the pressure of the pressure medium increases in the Line 117 and on the piston top of the thrust cylinder 80. The valve 147 is on the pilot or This pressure is applied to control line 149 and is when the pressure on the control line 149 is reduced to a value due to the previous setting of the valve

147 certain pressure, for example to 35 at, has risen, switched from its blocking position shown in the drawing to passage β division, in which a direct connection between lines 117 and 118 is established. This connection is a bypass so that no more hydraulic fluid reaches the thrust cylinder until another change occurs.

During the time in which the valve 147 is operated in the manner indicated above and a bypass closes to the thrust cylinder, the control valve remains

148 closed in order to maintain the pressure acting on the piston surface and a steady decrease

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wait for directed force to act on the drilling tool permit. If drilling continues and the drilling tool continues to penetrate the ground, it will fall this pressure off, as the cuttings on the worm rims of the drill moves upwards and the piston in the Thrust cylinder is moved downwards by a corresponding piece. When the pressure coming through the control line 149 is supplied to the valve 147 as control pressure a second, preset operating pressure of, for example, 26.5 at has dropped, the valve reverses 14? turn back into its locked position. As a result, the bypass between lines 117 and 118 is interrupted, so that a larger amount of pressure medium can reach the top of the piston of the thrust cylinder 80, whereby a further step of the drilling process is carried out will.

In the event that the operator uses the drilling tool to lift a short distance from the bottom of the borehole, this is done by operating the overdrive valve 111 in the manner described above, with of course the rotary movement of the drilling tool being switched off. The control valve 148 be set so that it opens in the opposite direction (from right to left in the drawing) when it via a control line 150 with the

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Bridge on the piston rod side of the thrust cylinder 80 is applied. If the operator has this option, he brings the valve 124 · into the reverse position (parallel arrows) and thus makes the line 118 the supply line and closes the line 117 to the tank return line 104. That Hydraulic fluid flows to the piston rod side of the thrust cylinder 80 and increases if the pressure is maintained on the top of the piston via line 118. This pressure increase is by means of the valve 148 over the control line 150 is measured and the valve 148 opens, as soon as the pressure in line 150 has reached the set Has reached reverse operating pressure, e.g. 7 at. The one on the top of the piston of the thrust cylinder under pressure Maintained flow medium flows via line 117 and valve 148 to the pressure medium container until the Control valve 124 'returns to its neutral position. (Valve 147 is off during this reverse operation, since it is constructed so that there is only one sighting of hydraulic fluid, in the present Pail allowed from line 117 to line 118.)

From the above explanations it follows that the pilot operation of the control valve 148 gives the operator the opportunity to lift the drilling tool as well also to turn the drilling tool in the opposite direction,

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which is sometimes useful for freeing a stuck drilling tool. It can also do this way The drilling tool is given a short upward push, sometimes resulting in the release of a stuck drilling tool necessary is. The normal drilling positions of the rapid traverse valve 111 (neutral) and the rotary motor valve are thereby used 112 (held in the clockwise rotation position) is not disturbed, so that there is no delay in the Drilling operation takes place

When the automatic control device according to FIG. 1 has also been described in connection with a drilling tool is, which is driven into the earth by means of a thrust cylinder arranged above this, it is without further understandable that the same automatic control devices can be used in a traction drill, e.g. Extension drill, or a reciprocating drill, in which a drilling tool is pulled down through a pilot shaft can be used. In these devices, the piston rod side of the push cylinder is during the high pressure side of the drilling process, while the auger shown, the piston top of the cylinder is the high pressure side during the drilling process. Around to convert the circuit according to FIG. 5 to use with an extension drill or a lifting drill, only need the connections of lines 117 and

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118 can be interchanged with the thrust cylinder 80 by, for example, instead of the line 103, the line 105 ' and instead of the line 110, the line 110 * is connected. To this possibility also in the claims to indicate is that side of the thrust cylinder, which is connected to the inflow line during the drilling process, as the drilling pressure side and that with the Tank return line connected side simply referred to as the other side.

When the drilling tool is loaded to full capacity, the operator gives the operating handle for the Langeamgang valve 124 (or 124 · ') free, and this returns to the neutral position under the action of the return springs (valve 124 'must be manually operated from the lower operating position to the neutral position be moved). The operator also places the overdrive valve 111 in the reverse position (in the Drawing on the left, symbolically represented by the crossed arrows) and holds it in this position, in which the lines 118 and 116 and the supply line 103 are connected to the bottom side of the thrust cylinder 80, and in which the top of the cylinder is connected to lines 117 and return line 104. Since the piston 83 at this time was near the bottom of the cylinder 80 (on the left in the drawing)

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1st come, the reverse flow causes the drilling tool to be withdrawn upwardly out of the borehole. That Foot pedal operated valve 109 is normally also held in the forward position at this time by tandem switching the pump section 13b with the pump section 13c to receive an additional pressure medium flow, whereby the speed with which the drilling tool is pulled out «can be increased. It is particularly emphasized that valve 112 has not been established since the start of the drilling cycle and has been locked into place remains in its initial forward position. The movement of the valve body 114 of the valve 111 in its The reverse position blocks any hydraulic fluid inflow to the motor 50 and therefore keeps the rotary movement of the Drilling tool by introducing a lock 119 in the supply line 103 as well as in the forward position of valve 111.

When the drilling tool is completely sucked out of the borehole, the actuating lever would be released of the valve 111 is the only measure that the operator still has to do, whereupon the valve body 114 moves into its neutral position under the action of a spring can return. All of the hydraulic fluid flow is immediately exerted by valve 111 and thrust cylinder 80 about the one that is still in the forward position

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Valve 112 including rotary motor 50 diverted. The foot operated valve 109 is still in its forward position, Un to increase the speed by using the auxiliary pump section 15b so that the rotor can be operated with the Driving rod 60 and the drilling tool 70 is accelerated accordingly quickly. That on the snails " walked 72 of the drilling tools is collected drill cuttings quickly ejected from the hole, whereupon the operator by again actuating the overdrive valve 111 in its forward position a new one Prepared for drilling process. The pump section 13b is kept connected to the supply line 103 via the foot-operated valve 109 until the drilling tool reaches the bottom of the borehole again.

It is emphasized that valve 112 controlling rotary motor 50 can be left in its forward position throughout the drilling cycle and for many other drilling cycles, typically until the borehole is advanced to the desired depth. The same direction of rotation that is used when drilling is usually used to eject the cuttings from the hole. The reverse direction of rotation is only used in the event that the drilling tool is stuck and has to be turned back or when the drilling tool is made of tough, sticky cuttings

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must be freed. In the latter case, the drilling tool is quickly raised above the borehole in order to to shake off the cuttings. Ea should also be mentioned that the cross connection I5I of the valve 112, which the lines 154 and 155 running between the valve and the motor are only then present is when valve 112 is in its illustrated neutral position. Venn the valve against it either is in the forward or reverse position, connection 151 and lines 154 and 155 are dropped are like the other valves without such a connection I5I with the supply and return lines 103 and 104 connected, as indicated by the arrows. The connection 151 has the task of a to form a closed line loop for the hydraulic medium passed through the motor 50, because if the lines 154 and 155 are suddenly blocked, the motor rotation would otherwise suddenly stop, and the brief torque changes could lead to considerable damage.

Using the hydraulic motor described in more detail above, the invention with the following characteristics was shown in implemented in practice:

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Drill diameter

maximum 1.22 m

Borehole depth usual: 2.44 - 3.66 m
maximum: 7.6 m kg Center distance 4 m. kg Gross weight of the
Year stuff 9 100 Weight of the drill
device together with
equipment 5 670

Height above ground

Height of the erected drilling mast

Drill rod dimensions

Machine output at 2,200 rpm

Torque on the boring bar

Turning speeds:

Drill

Pull out feed:

Fast

Slow thrust lifting speed 3.66 m model, 3.05 m 7 m model, 3.59 m

3.66 m model, 7 m 6.34 cm square 104 hp 620 kpm at 140 at

65 rpm 140 rpm

35 m / min 5.5 fc / min 5 670 kg 52 m / min

909886/0224

The drilling device was described above in connection with an overall hydraulic system, but it goes without saying that the measure of direct drive coupling is not limited to such a hydraulic system. Any motor can be arranged so that its axis is vertically in coaxial alignment with a drive rod and a thrust cylinder. The motor must have a high torque at low speeds, and its shaft must be provided with a non-circular axial opening which can accommodate a driving rod of appropriate cross-section and allows its axial movement. An electric motor which satisfies the above requirements may also come to Slneatft as suitable pneumatic motors. The lifting cylinder can also be acted upon by suitable other pressure means, and a suitable different door direction can also be used to apply the thrust force.

The combination of the hydraulic control devices is also not limited to the special drilling device shown here, i.e. the direct coupling of the motor, although it has the greatest advantages in this context. Known drilling devices that have a hydraulic rotary drive for the drill rod or the driving rod and a hydraulic drive for the advance of the driver

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contractor _rod-t provide can be advantageously combined with the inventive valve control, although they provide a mechanical coupling between the drive assemblies and the driven parts.

The one used to control the supply and discharge of fluid used for the thrust cylinder and the rotary motor Valves can also be constructed differently than the two valves 111 and 112, which are shown in Pig. 4 are shown. ' For the For purposes of the invention, valve 112 can be omitted entirely since its primary functions are in creation a direction of rotation reversal and in its neutral position lie in the complete stop of the engine. The last-mentioned function can be fulfilled by switching off the pumps. In addition, a single valve can control the in SIg. 4 and replace valves 111 and 112 shown fulfill all of the functions of these two valves when there are correspondingly more positions or auxiliary sventilen and Control lines is equipped.

909085/0224

Claims (1)

! 900210 Expectations 1. Hotary drilling jig with an at an angle drill rods held to the ground, a drilling tool attached to its lower end, furthermore with a rotary drive for rotating the drill rod and the Drilling tool and with a thrust drive which presses or drives the rotating drilling tool into the ground via the drill rod, characterized in that the rotary drive is a motor (50) directly coupled to the drill pipe (60); that the drill rod has a non-circular cross-section at least over part of its length and the motor shaft (51) designed as a hollow shaft has at least one rope of its length has an axial opening with a correspondingly non-circular cross-section, in which the non-circular part of the drill rod is positively guided and axially sliding under the influence of the thrust drive (80) 909885/0224 2. Apparatus according to claim 1, characterized in that the thrust drive is one above the motor (50) coaxially to this arranged, long push cylinder (80) in which a piston (83) is slidably disposed between the cylinder ends; and that that Drill rod (60) engages with its upper end in the thrust cylinder and is connected to the piston and runs down from the cylinder and through the Longitudinal opening of the motor shaft (51) in a fixed rotational position is carried out slidingly to this and axially in it. τ. 3. Apparatus according to claim 2, characterized in that for actuating the drilling device, a hydraulic supply and control system with a valve device (111, 112) for controlling the rotary movement of the hydraulic motor (50) and the up and down movement of the piston (83) the hydraulically operated thrust cylinder (80) is provided; and that the valve device can be adjusted to at least a first position in which the hydraulic medium presses the piston of the thrust cylinder downwards and the hydraulic medium flow to the total motor is blocked , and in a second position in which the hydraulic medium flows through the motor and not through the thrust cylinder is conducted, the drill rod (60) and the drilling tool (70) in the first position of the valve device without rotating movement. 903885/0 * 24 -X- is lowered until the drilling tool touches the ground and after switching from their first »to their second position it is set in rotary motion. 4. Apparatus according to claim 3 »characterized in that defl the Ventilvorrlohtung (111, 112) in a third Position is adjustable in which the thrust cylinder (80) in the piston upward direction with the hydraulic medium acted upon and the Kotary-Hotor (50) not acted upon is, so that the drilling tool (70) from its drilling engagement without iteehbewegung solely by adjusting the Valve device is lifted from the second to the third position « 5 · Device according to claim 4, characterized in that the drilling tool (70) has a (72) the drill cuttings conveying twist or auger, which the drill cuttings in the third position of the valve device (111, 112) to the surface of the earth transported and when changing the Vontile device into the second position near the drill parts on the Järdbodon unloads. 6. Device according to one of claims 3 to 5, since * characterized in that the valve device is composed of two separate valves (111, 112) from 909885/0224 1300210 which the first (111) blocks the hydraulic fluid supply in a first ventilator position around the stroke (80) and the hydraulic medium leads to the second valve (112) and, in a disputed valve position, the hydraulic cylinder acted upon in the piston downward direction with hydraulic medium and the hydraulic fluid flow sum to the second valve and sum Rotarjr-Hotor (50) locks; and that for the »wide Valve (112) at least a first valve division dead " is seen in which a flow path for the 'hydraulic medium of the first valve sum rotary motor is formed, the drilling tool (70) in its normal Direction of rotation is moved} and that the drilling tool in the "wide valve position of the first valve and in the first valve position of the second valve without turning «· Movement from a raised position above the soil until it touches the ground can be lowered and then as lein by switching the first valve from its second to the first position while diverting the hydraulic means from the thrust cylinder to the aotary motor in Earth contact is rotated. 7. Device according to claim 6, characterized in that a third valve position is provided for the first valve (111) in which the hydraulic medium * inflow sum to the second valve (112) and to the rotary motor (50) locked and the hydraulic fluid to the thrust cylinder 909885/0224 (80) is directed in the piston upward direction, wherein the The drilling operation of the drilling tool (70) is interrupted and this can be lifted out of the borehole without a rotary movement » Θ. Device according to claim 7 »characterized in that that the hydraulic supply and control system can be actuated by an operator to control the hydraulic fluid flow through the thrust cylinder (80) second valve device (Fig. 5) and an automatically operating, the pressure on the drilling pressure side of the cylinder controlling and limiting valve device (14-7, 148); and that the automatically operating valve device is provided with a normally closed controlled pressure relief valve (147) and with the hydraulic lines (117 »118) connecting the second valve device to the thrust cylinder a üuntrollventil (148) is provided, which is in the the hydraulic line connected to the drilling pressure side of the thrust cylinder is located and allows the inflow to the thrust cylinder, the overpressure valve (147) over a control line (149) with the pressure at the drilling pressure * - side of the thrust cylinder is acted upon as control pressure and is set to passage when this pressure is the exceeds the preset control pressure threshold. 9 0 9 8 8 5/0224 9. Apparatus according to claim 8, characterized in that that the second valve device (Fig. 5) is reverse flow direction of the hydraulic medium through the thrust cylinder (80) can be reversed; and that that X control valve (148) via a control line ■ picked up with a tone from the other hydraulic line (118) Control signal applied and operated so that it allows a flow in the reverse direction. 10 · Device according to claim 5, characterized by a »wide hydraulic valve device (109) with which the slope of the sliding drive (80) and rotary drive (50) rotating via the first valve device (111, 112) sub increasing the axial and Rotation speed of the drill pipe (60) can be increased. 11. The device according to claim 3, characterized in that the valve device (111, 112) in a third Position adjustable in which the thrust drive (80) in such a direction with the hydraulic medium is applied that the drill pipe (60) and the drilling tool (70) are raised, and in which the Hydraulic fluid flow to the rotary drive (50) separated is, so that simply by switching the valve device from the second to the third Ventilstellimg the 9 09 885/0224 Rotational movement of the drill rod and the drilling tool stopped and the drill pipe and the drilling tool can be lifted out of the borehole * 12. The device according to claim 3 * characterized in that the valve device is a first valve (111) and a second valve (112), the first valve blocking the operating fluid flow to the thrust cylinder (80) in a first valve position and releasing it to the second valve C112) and in a second valve position the operating fluid flow to the scraping cylinder (80) releases and blocks the second valve, and at least one first valve position is provided for the second valve (112), in which the flow of operating medium is released, so that the drilling tool (70), starting from a position at a distance above the bottom of the borehole a to the bottom of the borehole can be lowered and rotated with the simultaneous application of a thrust force by first nodding the first valve into its wide ventilating position and the second Valve are brought into the first valve division, including bringing the drilling tool into contact with the ground, and that first valve is then switched into the first valve division. 909885/0224 13. Device according to Claim 1, characterized in that the push cylinder (80) is a double-acting Piston-cylinder unit 1st, which seldom with the two pistons to swel the operating agent is supplied under the control of an automatically operating valve device and hydraulic lines (11?) 118) discharging into a container (14) are connected so that the automatic working valve device a controlled * pressure relief valve connected between the hydraulic line pair (14-7), which the pressure of the drilling pressure side of the cylinder via a control line (149) is supplied as control pressure, which is normally in the closed position, the connection between the hydraulic lines is interrupted, and which at a certain control pressure on the control line (149) is opened, with a flow of operating medium from the hydraulic line located on the drilling pressure side of the cylinder is let through to the other hydraulic line; that the pressure relief valve (147) at a certain smaller Control pressure on the control line can be switched back to the closed position; and that a control valve (148) in the nit the drilling pressure side of the thrust cylinder Connected hydraulic line is located, which allows an operating medium to flow to the drilling pressure side and one Block outflow of resources from this. 14. Device according to. Claim 15 «characterized in that the overpressure valve (147) is switched from the closed position to the open position during a drilling gate B when the pressure on the drilling pressure side of the thrust cylinder (80) has reached the first predetermined level, the operating medium from P of the supply line (107) diverted into the tank return line (104), a bypass to the Bohrdruckeeite the thrust cylinder is formed and a further increase in pressure on the drilling pressure side is prevented; that this Control valve (148) prevents the operating medium from flowing out of the Bohrdruokseite of the thrust cylinder, so that there is a constant thrust from the operating medium enclosed on the drilling pressure side of the cylinder is exerted on the drilling tool (70) until it is advanced, whereupon the pressure of the enclosed Equipment »drops to ftu the second specified pressure level at which the control line (149) the pressure relief valve connected to the drilling pressure side of the thrust cylinder switches to the closed position, the Bypass interrupts and allows a renewed inflow to the drilling pressure side of the stroke cylinder. 15 · Door direction according to claim 14, characterized in that the rolling valve (148) is switched so that there is an outflow of the operating fluid from the drilling pressure side of the thrust cylinder (80) allows it, over a control line (150) the pressure of the other side of the cylinder is supplied as control pressure; that the automatically operating valve device (111, 112) is suitably set up for Ua control of the application of the thrust cylinder, the drilling tool (70) except Drilling engagement is brought when the hydraulic lines (117t 118) are reversed in polarity such that the drilling pressure side dds thrust cylinder to the container return line (104) and the other side is connected to the supply line (107); and that the control valve is operated as soon as the bridge located on its control line (14-9) and removed from the other side of the thrust cylinder has reached a certain operating pressure, in which the control valve daa allows operating medium to pass through to the tank return line (104). 16. Rotary drilling jig with one at its lower End with a drilling tool provided with a drill rod, with a hydraulic rotary drive, which sets the drill rod in rotary motion and thereby allows its longitudinal movement, and with a hydraulic thrust drive, which moves the drill rod in the longitudinal direction, characterized by a hydraulic timing and control system (Fig. 4-, 4A, 5) with a rotary drive (50) and the valve device controlling the thrust actuator (80) 909885/0224 (111, 112), for which at least one first valve position is provided, in which the thrust drive is acted upon in such a direction that the drill rod (60) and the drilling tool are lowered , and in which the flow of hydraulic fluid to the rotary drive is blocked, and for a second valve position is provided, is acted upon aer the rotary drive (50) and the linear actuator (80) unstressed. 909885/0 2.2 Blank page