DE7246553U - Hydraulic control device for moving a working piston, in particular for a hammer drill for drilling earth or rock - Google Patents

Description

PATENT AGENCIES , \\, '·.,' · A .. '.' .. 'I.'. '., J?

DR.-ING. BY KREISLER DR. -ING. SCHÖN WALL

DR.-ING. TH. MEYER DR.FUES DIPL-CHEM. ALEK VON KREiSLER DIPL-CHEM. CAROLA KELLER DR.-ING. KLDPSCH DIPL-ING. SELTINS

KDLN 1, DEICHMANNHAUS

Dec. 19, 1972 Sg-Is

Engineer Günter Klemm
Special company for drilling technology 596 Olpe / Wenkhausen

Hydraulic control device for moving a working piston. <3, in particular for a hammer drill for earth or rock drilling

The invention relates to a hydraulic control device for moving a working piston, in particular for drilling jigs for drilling holes in the ground or in the mountains, primarily for one Deep hammer drill, with a cylinder surrounding the working piston, with inlet openings at different heights and has outlet openings for the pressure fluid, and with at least two mutually movable Control parts that release fluid passages into the interior of the cylinder in certain positions, in that their tax openings coincide with each other.

In the case of earth or rock drilling, additional impact energy is used to rotate the drill string. The blows are usually from one applied with a compressed air hammer.

. In known hydraulic control devices is the The cylinder surrounding the piston is connected to a control unit which contains valves and slides which, according to Can be operated according to an external control system. The control unit can be structurally connected to the cylinder

which should be appropriate. However, this has the disadvantage of a complicated line routing and requires components which are extremely difficult and expensive to manufacture. In addition, such control devices are in precision work are made, very susceptible to malfunctions and vibrations. This is particular then of importance when the piston is used to operate a hammer drill or a striking tool or the like shall be. Such devices are used in rough operation and should therefore be used as little as possible be susceptible to malfunctions and soiling.

The object of the present invention is to create a control device of the type mentioned at the outset, which takes these requirements into account and is therefore simple and robust in construction, but at the same time is able to bring about extremely fast piston movements.

• To solve this. Task is proposed according to the invention, that the control parts consist of an inner cylinder arranged coaxially around the piston and one the The inner cylinder surrounding the control sleeve exist.

According to the invention, the control parts are arranged around the piston, with even the actual cylinder, in which the piston moves, can represent one of the two control parts. The control parts become relative moved towards each other, so that their control openings are alternately brought into congruence to the respective 'To bring about the necessary piston movement by admitting hydraulic fluid.

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The concentric arrangement of the control parts to the piston has the advantage of a compact design without to have to make the individual parts too small. There is also a direct connection from the Pressure source to the cylinder space without the interposition of long lines, so that the individual movements of the Control modules can directly influence the pressure conditions in the cylinder without any time delays. this makes possible extraordinarily rapid movements of the dolly.

The speed of the piston movements is also promoted by the fact that the control openings are relatively can be made large so that they have a large throughput in the open state. the The device is therefore particularly suitable for moving heavy working pistons, such as those used in rotary hammers, for example or the like. Are required. Numerous other types of application are of course also possible.

Compared to the air or steam drives normally used in heavy hammers has the inventions ^': dung modern hydraulic control device for a ·' working piston, which causes at the same time the plunger driver, the advantage of less Geräuschentv; ieklung and the further advantage of considerably lower operating costs.

The control device can be designed so that the inner cylinder and the control sleeve can be rotated relative to one another about the longitudinal axis of the working piston are, and that cooperating control openings on both control parts in each case are arranged at the same heights. The tax movement

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So is a rotation of one of the two control parts, which both have an essentially tubular shape and lie one inside the other. One control part, for example the control sleeve, is freely rotatable, while the other Control part, for example the inner cylinder surrounding the piston, is mounted non-rotatable. In particular Angle of rotation positions of the control sleeve, the openings on both control parts lie one above the other, so that pressure fluid from the outside through the two control openings through into the cavity of the inner ylindens can flow to move the piston.

Another possibility of implementation is to that one of the two control parts is fixed, but the other is axially displaceable, and that cooperating Control openings at least partially in the same angular range are arranged. The displaceable control part is moved back and forth in the displacement area, wherein the individual control openings to the inner ravmi deJ3 inner cylinder. one after the other in certain Open the sequence so that the hydraulic fluid flows in or can flow out. The relative movement of the two control parts can also be a screw movement exist, in which the movable control unit! 1 both a rotation and a translational displacement executes.

A preferred embodiment of the invention is with provided with an inner cylinder, which with respect to a surrounding the control sleeve, the housing of the control device ' direction forming outer cylinder is fixed, with the SteuerhUlsfe between inner cylinder and outer cylinder

is rotatable at least in an angular range. In such a control device, the control sleeve can be connected to a rotary drive, the speed of which is optionally variable, so that the control frequency and thus also the stroke frequency of the working piston can be influenced by adjusting the drive speed. This is extremely important for a number of application cases. So when Ge stone holes must be drilled 10 stroke rate occasionally relatively high ■ while other floors require a slower impact sequence. If the he-Ii .. inventive control device in a hammer drill

|:. plant used, then you can see the stroke ratios

, easily by changing the drive speed to the

15 Match the correct sequence of strokes.

The same is the case when you are stuck with it

Control sleeve and rotating inner cylinder, which lies between [ control sleeve and working piston, works.

In the case of rotary adjustments, however, the adjustment movement does not necessarily have to be a constant rotation, rather, it is sufficient to turn the control part, which can be rotated in each case, back and forth in an angular range.

A preferred type of drive for the control device and the working piston itself is the turbine drive in places that are difficult to access. When using a Turbine drive, the power for the drive can come from the same pressure source as that via the 'Control parts caused the cylinder surrounding the working piston to be fed.

So all the energy is in the form of hydraulic fluid fed. This causes both the drive of the control device and the displacement of the working piston. The turbine drive can consist of one or more Ren nozzles exist, which the pressure fluid against one provided on the control sleeve or on the inner cylinder Inject blading and thus set the relevant part in rotation. A preferred application for such a design of the drive direction are deep-hole hammers, which in the course of a drill string close to the drill bit, i.e. inside of the borehole, are arranged, and their impact. gie transferred to the drill bit as undamped as possible shall be. Such downhole hammers can be designed so that they do not protrude laterally over the drill pipe and thus fit well into the linkage. The hydraulic fluid is supplied from above via the (hollow) drill pipe.

In such a deep hole drill 'the outlet line of the turbine drive and / or the outlet line of the Cylinder in which the working piston moves, guided down in the housing to the drill bit. The drive fluid can act as a detergent at the same time of the drill bit after it has passed through the control ports and the cylinder space is, or after it has left the turbine drive.

In a further expedient embodiment of the invention, the working piston displaces during its axial movement The inner cylinder or the control sleeve into one via a screw guide with a steep incline

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reciprocating rotary movement in which the control openings on both control parts periodically coincide come together. Part of the vigilance is possible up and down with the working piston and shifts the counterpart of the viewing shaft guide into a reciprocating motion Rotary movement, which in turn controls the piston. Overall, this is an oscillatable system whose oscillation frequency depends on the working pressure of the hydraulic fluid and on the accelerating mass of the working piston is influenced. Due to the special type of self-control of the .Working piston ensures that the working piston always performs complete strokes. At this . The type of control device always works with a constant piston stroke, while the externally driven ones Control devices, both in the motor-driven device and in the turbine drive Depending on the drive speed, smaller strokes with high frequency or large strokes with low frequency can be executed.

If, with an external drive, several strokes are carried out with each revolution of the rotatable control section then the control part must cyclically distribute several sets of control openings over its circumference exhibit.

The control openings on one of the control parts, preferably on the fixed control part, can be used as Slots may be formed to ensure that the piston is driven for a sufficient period of time becomes, in order to at least approximately reach its end position. The slots can be in the central area

be further than at the ends, in order to reduce the piston acceleration, which should be largest in the middle area of the piston path, to be removed towards the ends.

The control sleeve can have a further longitudinal groove or bore with two radial bores for discharge of the hydraulic fluid.

The invention is described below with reference to FIG the figures explained in more detail using some preferred exemplary embodiments.

Fig. 1 shows a first embodiment of the control device with an external motor drive in longitudinal section,

FIG. X shows the inner cylinder of the control device according to FIG. 1 in side view and

Pig 3 shows the control sleeve of the control device of Fig. 1 in side view.

Fig. 4 shows an end view of the control sleeve.

^'7 * piston position can be seen FIGS. 5a to 5d show sections along the line aa, bb, cc and dd in Fig. 1, from which the positions of the control parts shown in in Fig. 1.

6a to 6d show the same cross-sectional views when the piston is out of its stroke position should be pressed down and the tax sleeve. compared to the illustration in Fig. 5 by 180 ° world heritage

turns is.

Pig. 7 shows a second embodiment of the control device, only those parts are shown which differ from the embodiment according to FIG. The control sleeve is driven by the working piston via a screw guide.

Pig. 8 shows a section along the line VIII-VIII of Figs. 7 and

Fig. 9 shows the rural design of the control openings on the inner cylinder in the embodiment according to FIG.

Fig. 10 shows a third embodiment of the control device, in which a turbine drive is used.

FIG. 11 shows a top view of the control device and FIG. 12 schematically illustrates the turbine drive.

Fig. 15 shows a longitudinal section of the control sleeve at the embodiment of Fig. 10 and

FIG. 14 shows a top view of the control sleeve according to FIG. 13.

In the embodiment shown in FIGS the control device is the working piston kit 10 designated. The working piston is arranged in the tubular inner cylinder 11 and in this Can be moved lengthways. With its piston

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surface 12 it lies on the cylindrical wall of the inner cylinder 11 at.

At the upper end of the inner cylinder 11 is a sliding bush 13 and at the lower end a cylinder liner 14 is provided, which serve to guide the working piston 10 and interact with ground piston surfaces 15, 16. In the area of the ground surfaces 15, 16 and the Piston surface 12 are each provided circumferential annular grooves of small depth, which on the one hand the lubrication and on the other hand serve to seal the working piston.

The cylinder liner 14 is connected in an axial direction device down a pressure plate 17 and an end plate 18 through which the piston rod 19 passes. A sealing ring 20 is let into the end disk 18

The control sleeve 21 encloses the inner cylinder 11. It has essentially the shape of a tube that is attached to his upper end is tapered stepped and there to the rotating shaft 22 of a variable speed Hydraulic motor 2 ^ is connected - The control sleeve 21 is at its lower end with an axial roller bearing 24 on an outer flange 25 of the inner cylinder 11 supported.

The control sleeve 21 is surrounded by the housing 26. This consists of a substantially tubular Middle part 27, the top by a hydraulic motor .23 supporting hood 28 and bottom by a plate 29 is closed, through which the piston rod 19 back

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11I _1. , .- ι tilt

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protrudes through. The plate 29 supports the end disk l8.

The pressure line 3JO leads into a thickened one Area 31 of the housing 26 and opens there into a circumferential annular groove 32. The control sleeve 21 is provided on its outside with longitudinal grooves 33t 3 ^, which are offset from one another by 180 °, and those in the area of the annular groove 32 of the housing end up. The longitudinal groove 33 leads into an area down below the. The lowest position of the piston surface 12 is located. Here is a 35 in. Radial hole the groove 33 is provided. . . ■

There is also a radial bore in the groove 34 36 (Fig. 3) »which are arranged above that point is that the piston surface 12 can occupy with the greatest piston stroke, the radial bores 35 »36 form the control openings of the control sleeve 21, via which the pressure fluid is supplied. To the outlet the hydraulic fluid is a control sleeve in the dtr Longitudinal bore 37 is provided, which the longitudinal grooves 33 * 34 protrudes upwards and opens into an annular space 38 formed between control sleeve 21 and housing 26, from which an outlet line 39 from the Housing leads out. From the longitudinal bore 37, two transverse bores 40, 41 lead out of the inner wall of the control sleeve out. The transverse bore 40 lies - apart from the angular position - above the radial bore 36 and the transverse bore 41 below the radial bore 35. The longitudinal bore 37 is at 45 ° with respect to the longitudinal groove 34 offset (Fig. 4). Located at the level of the Ouerbohr 41 on the inner cylinder a horizontal

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Slot 43, which sioh extends over an angle of approximately 84 °. A further slot 44 is arranged opposite this slot at the level of the transverse bore 40. The two slots 43, 44 represent outlet slots, as will be explained. With respect to the outlet slots 43, 44 offset by 45 ° are two superimposed Inlet slots 45 »46 arranged at the level of the radial bores 35 and 36 of the control sleeve 21 lie.

While the control sleeve 21 inside the housing 26 is rotatable, the inner cylinder 11 is fixed non-rotatable. This is done using a cylinder pin. 47, which from below through the earth disk 18, the pressure plate 17 and. the splash of the cylinder liner 14 is inserted through into the flange 25 of the inner cylinder.

In the mutual assignment of control sleeve and inner cylinder shown in Fig. 1, their different Positions in Figs. 5a to 5d are shown, the radial bore 35 of the control sleeve is above the Slot 45 of the inner cylinder. In this way, pressure fluid flows from the pressure line 30 through the Longitudinal groove 33 and the control openings 35, 45 therethrough into the space below the piston surface 12. The space above the piston surface 12 is sealed against the high pressure side, since the slot 46 is located on the Radial bore 36 facing away from the side. Since the working piston is therefore not opposed to any counter pressure is, it is raised because there is also no connection between the lowest slot 43 and the longitudinal bore 37, which forms the outlet channel. The one above the

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Pressure fluid located on the piston surface 12 escapes through the uppermost slot 44 and the transverse bore 40 into the outlet channel 37 and from there via the annular space 38 into the outlet line 39. While the working piston 10 rises, the cylinder liner 21 is rotated further by the hydraulic motor 2} . In the process, the supply of liquid through the control openings 35 * ^ 5 is interrupted, so that the working piston is no longer lifted; all passages remain closed over an angle of rotation of about 12 ° until the situation shown in FIG. 6 arises in principle, in the case of the pressure fluid penetrates through the longitudinal groove J> k and the slot 46 into the cylinder space above the cylinder surface 12. The control openings 40, 44 are not in congruence with one another, so that the pressure fluid cannot escape from this space. The working piston 10 is pressed downwards, and the liquid displaced thereby is pressed through the slot 43 and the transverse bore 41 into the outlet channel 37. In this position, the passage through the control openings 35 » 45 is blocked.

It can therefore be seen that, depending on the angle of rotation of the control cover, * 21 an actuation of the Working piston 10 takes place.

In the embodiment described, the working piston 10 is used to move a hammer mass 48, which is attached to the lower end of the piston rod 19. To make the stroke movement particularly effective, If the piston rod is preferably above the effective

seed piston surface 12 thinner than below this piston surface. This is the contact surface for the hydraulic fluid larger when moving down than when moving up. The consequence of this is that the working flask is raised relatively slowly in order to then be depressed with great force.

From Fig. 2, the shape of the slots 4} to 46 can be seen. It can be seen that the slots are widened in the central area. The purpose of this is to enhance the interior of the Inner cylinder 11 then supply the largest amount of hydraulic fluid when the working piston is about is in the middle of its stroke.

The inner cylinder 11 with a certain slot shape wheel certain slot dimensions can easily against another inner cylinder can be exchanged, for example to increase the stroke of the working piston to obtain. Since the control sleeve 21 is forcibly guided by the external drive, the strokes of the working piston are made at the frequency determined by the drive executed. The amplitude of the stroke depends on the length of the slot or that amount of liquid which flows through the control openings in the rotational range of the slot.

The control device can form the head of a drilling device which continues from the plate 29 downwards. This is in Pig. I indicated by dash-dotted lines.

In the modified embodiment according to FIG 9, on the other hand, there is a forced guidance of the control sleeve in the sense that the working piston is always full performs constant strokes with full amplitude. In contrast, the stroke frequency of the respective pressure and the KoP.ben load determined.

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In the embodiment according to FIGS. 7 to 9, the structure and operation of the control except for the parts described below is the same as means in the embodiment according to FIGS. 1 to 6. This, in that the inner cylinder 11 is non-rotatably to the working piston 10 is arranged around and the working piston slides up and down in it, while the control sleeve 21 is able to perform rotary movements.

The cap 28 'of the housing 26 of FIG. 7 is at the top Formed closed at the end. It has a cavity 50 into which a multi-splined shaft 51 with a helically wound spline runs, which is at the upper end of the ... .. ' Working piston 10 is mounted in its extension, penetrates with each piston stroke. The grooves of the multi-spline shaft 51 have a relatively small slope of, for example, 5 ° # to keep the friction low keep. They engage in a nut 52 fastened to the upper end of the control sleeve 21. Through suitable Means (not shown here) ensure that the piston 10 moves in its up and down movements cannot twist, via the screw guide 51 »52 therefore, with each up and down movement of the working piston, the guide cylinder 21 becomes a reciprocating motion Rotary movement granted. This is sufficient to cause the control openings for the pressure fluid be opened and closed in the manner explained with reference to FIG.

Around the control openings during the angular rotation of the control sleeve with a large opening cross-section on top of each other. bring the control ports on the inner cylinder

724655330.8.73 ^'16 "

11 expedient travel in the ir; Fig. 9 shown Way designed as elongated holes 53, which are perpendicular with a slight incline. The associated Control openings on the control sleeve are also designed as elongated holes and not as bores as in the exemplary embodiment of FIG. 1.

In the control device shown in FIGS. 10 to 14, a control head 56 is screwed to the lower end of a hollow drill rod 55. A passage 57 passes through the control head 56 in the vertical direction. This leads to a vertical groove 58 which is worked into the control sleeve 59. The control sleeve 59 is rotatable in a housing 60 about its vertical axis. The housing 60, like the control head 56, has cross-sectional dimensions which correspond to those of the drill rod 55, so that the two parts mentioned can be attached to the drill rod without protruding laterally. The housing 60, which _λ is essentially in the form of a tube, is fastened to the control head 56 by a series of vertical screws 61.

The rotation of the control sleeve 59 around the Irish cylinder 62 around and in the housing 60 is carried out by a turbine drive. This is formed by nozzles 63 (Fig. 12), which are accommodated in recesses 64 on the underside of the control head 56 and act on a ring gear 65 which is located on the upper end face the control sleeve 59 is located. The nozzles 63 act approximately tangentially on the gear rim 05. They are at an angle of about 45 ° or less against the

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Vertical inclined. The teeth of the ring gear 65 are running nanh at the top and are also inclined according to the inclination of the nozzles 65, so that between they pockets 66 are formed into which the nozzles point, so that the ring gear 65 and with it the Control sleeve 59 in rotation around the vertical axis be moved.

The nozzles 63 are also fed via the drill rod 55. For this purpose, the control head ^ 6 is provided with vertical bores 67, which, however, only partially penetrate it and open into inclined bores 68 which are worked into the control head 56 from below from the recesses 64. The inclined bores 68 have a thread for screwing in the nozzles 63.

As FIG. 11 shows, there are a total of two nozzles with associated bores 67 which, based on the Toothed ring 65, are arranged offset from one another by l8o °.

The line 57, through which the liquid under a pressure of about 150 atmospheres in the grooves 58 arrives, initially opens into an annular space 69 provided at the lower end of the control head 56 from there to a total of four vertical grooves 58 on the outside of the control sleeve Corresponding to the four vertical grooves 58 take place with one revolution of the turbine-driven control sleeve 59 two up and down movements of the piston 70 instead. The inner cylinder 62, which is surrounded by the control sleeve 59

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give 1st, and in which the piston 70 is vertically displaceable, contains control openings 71 * 72, of which only two are visible in FIG. 10. When the control sleeve 59 rotates, the control openings of the inner cylinder come to converge cyclically with its control openings. The control openings are arranged in such a way that, in order to lift the piston 70, two control openings 71 * 73 always lie one above the other below the piston surface 70 and thus pressure fluid can reach under the piston surface 74 via the corresponding groove 58. At the same time, there is an overlap between the control opening 72 and a further opening 75 of the control sleeve above the piston surface JO. The opening 75 leads to a vertical bore 76 in the control sleeve, through which the fluid is diverted downwards. The vertical bore 76 forms the low pressure side of the control system.

When the piston 70 is raised, it acts in the grooves 58 The prevailing pressure via corresponding control openings not shown in detail here from above on the piston surface 70, while the space below the piston surface 74 with the vertical bore 76 connected. The piston 70 is therefore driven downwards by the high pressure, and that below the piston surface 74 existing liquid runs through the vertical bore 76 ao. With this last one The process is the control sleeve 59 compared to the position shown in Fig. In which the piston is driven up is rotated by 90 °. With a further rotation, the piston 70 is raised again.

J) O Fig. 10 shows a section along the line XX of

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Pig. 14 fig.

f) the piston 70 is provided at its ends with FUhrungszylindern 77 $ 78, which run in Oleitbüchsen 79th The Oleitbüchsen 79 are inserted into the inner cylinder 62. The guide cylinders 77 »78, like the control sleeve 59, have circumferential lubrication grooves of small depth, which ensure low-friction movement with good sealing.

The control head 56 is on its underside with a Provided cylinder bore 80 into which the control cylinder 77 protrudes when the piston 70 is raised. To liquid which may get into the bore 80, to be discharged and thus the formation of a counterpressure cushion, that would hinder the piston movement is to avoid the bore 80 as a ball valve formed pressure relief valve 81 is connected to a vertical bore 82 of the housing 60. The vertical drilling 82 is also connected to the annular space 83 in which the ring gear 65 of the turbine drive runs. The vertical bore 82 is at the lower end of the control device via a (not shown) Annular space connected to the vertical bore 76 of the control sleeve, so that the low-pressure sides of the turbine drive and the piston control are combined. From there, a line 84 leads into the adjoining one Part of the drill string down to drain on the drill bit 85. The hydraulic fluid, for example consists of water to which an oil emulsion is added, so it is used for the Piston drive or for the turbine drive as a flushing

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fluid used for the borehole.

The piston assembly shown in Figs forms a deep-hole hammer. The lower end of the piston has a hammer (not shown) or connected to an anvil that strikes against the drill bit 85 from above. The drill bit 85 is attached to the lower end of the drill rod 86 so that it cannot rotate and can be freely displaced in the vertical direction within limits .

If a pressure fluid acts on the control head 56 from above, the turbine drive is started. The control sleeve 59 is rotated and the piston 70 is moved up and down at a frequency determined by the speed of rotation of the control sleeve depends. is

I ^ this speed of rotation high, then the piston leads , Strokes with a relatively small amplitude, because the movement is reversed when the piston is only has traveled a short distance. If, on the other hand, the speed is slow, the working piston 70 carries jewels its full stroke. The number of revolutions can depending on the nature of the soil by inserting it different nozzles 63 or by connecting Droscel elements in front of the nozzles that you can work with either a high or a low beat frequency.

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Claims (18)

A η s ρ r U ehe 1. Hydraulic control device for moving an Arbelte piston, especially for drilling devices for drilling holes in the ground or in the J mountains, primarily for a deep hammer drill with a cylinder surrounding the working piston, the inlet openings and outlet openings at different heights for the pressure fluid, and with at least two movable control parts which are in certain Positions release fluid passages into the interior of the cylinder by their control openings come to coincide with each other, thereby characterized in that the control parts consist of a coaxially arranged around the piston (10, 70) Inner cylinder (11, 62) and a control sleeve (21, 59) surrounding the inner cylinder consist " 2. Control device according to claim 1, characterized in that the one Inner cylinder (11, 62) forming the control part with a cylinder surrounding the working piston (10, 70) is identical. 3. Control device according to claim 1 or 2, characterized in that the Inner cylinder (11, 62) and the control sleeve (21, 59) relative to one another around the longitudinal axis of the working piston (10, 70) rotatable around, and that cooperating control openings (e.g. 35, 45; 44, 40) are arranged at the same height on both control parts. - 22 4. Control device according to claim 1 or 2, characterized in that the Inner cylinder and the control sleeve relative to each other non-rotatable, but displaceable in the axial direction, and that interacting control openings at least partially in the same angular range are arranged. 5 · Control device according to claim 1 or 2, characterized in that the Inner cylinder and the control sleeve relative to each other are axially displaceable and rotatable at the same time in the form of a screw movement. 6. Control device according to one of claims 1 to J5 * characterized in that the inner cylinder (11, 62) with respect to one of the Control sleeve (21, 59) surrounding the housing (26, 60) of the control device forming outer cylinder .fixed, and that the control sleeve between the inner cylinder and the outer cylinder at least in an angular range is rotatable. 7. Control device according to claim 1, characterized in that the inner cylinder da3 is rotatable between control sleeve and working piston at least in an angular range. 8. Control device according to claim 3> characterized in that the control sleeve (21) or the inner cylinder (11) is coupled to a motor (23) and from this - possibly with changeable speed - is drivable. 9 · Control device according to claim 3 * thereby characterized in that the control sleeve (59) or the inner cylinder (62) from a turbine drive (Nozzles 63 and ring gear 65) is driven. 10. Control device according to claim 9 »characterized in that the feed of the turbine drive comes from the same pressure source as that via the control parts (inner cylinder 62 and control sleeve 59) caused the cylinder surrounding the working piston (70) to be fed. 11. Control device according to claim 10, characterized characterized in that the feed takes place via the pipe of a drill pipe (55), in the course of which an anvil that acts on a drill bit (85) through saw blades is actuated Working piston (70) is provided. 12. Control device according to claim 11, characterized in that the outlet line (vertical bonrung 82) of the turbine drive and / or the output line (vertical bore J6) of the cylinder in the housing (60) is guided downwards to the drill bit (85). 13 · Control device according to claim 3, characterized in that the working piston during its axial movement over a screw guide (51, 52) with a steep incline, the inner - 24 - - 24 - ■ ■. cylinder or the control sleeve set in a reciprocating rotary movement, in which the control openings on both control parts periodically to Coincide with each other (Fig. 7 »8). 14. Control device according to claim 3 *, characterized in that the inner cylinder (11) at the level of the control openings of the control sleeve (21) partially circumferential slots (43 to 46) having. 15 · Control device according to claim 14, d. a d u r c h g e k e η η ζ e i c h η e t that the slots-themselves Extend each over an "angular range of slightly less than 180 °. 16. Control device according to one of the preceding claims, characterized in that the control sleeve (21, 59) has a pair of longitudinal grooves (33, 34j 58) or bores offset from one another by an angle, each of which has at least one radial bore (35 * J6 ) zvm supplying the hydraulic fluid to the control openings. 17 · Control device according to claim l6, characterized characterized in that the control sleeve (21, 59) has a further longitudinal groove or bore (37 »76) with two transverse bores (40, 4lj 75) for discharging the hydraulic fluid. 18. Control device according to claim 13 * thereby - 25 - characterized in that the control openings in the control sleeve and / or the inner cylinder elongated holes (53) with predominantly vertical ones Components of their longitudinal axis are (Pig. 9) ·