DE385131C - Method and device for controlling the drilling feed rate in earth drilling rigs - Google Patents

Description

ISSUED
ON NOVEMBER 12, 1923

CLASS 5 a GROUP

(H 92538 VI \ ₅ a)

The invention relates to methods and devices for earth drilling rigs and the like. and relates in particular to an automatic adjustment of the boring mill according to the A resistance or the type of formation encountered by the drill bit during the drilling process.

An object of the invention is to provide a control method of those indicated above Type by which the regulation is exempted from irregularities, slippage, variable friction and the like, which occur in controls and drives by means of belts, Water pressure, steam, compressed air and friction devices can be found in the relevant Find technology use. The invention also provides a method such that that the mechanical forces that are made available during the regulation, their Do not change direction, d. H. the forces are never reversed, but only change her size. As a result, the disruptive effects of inertia are reduced to a minimum Brought to measure, vmff the scheme is independent of wear and tear and loss of movement in the facility. In this way, the invention creates a control method for earth drilling apparatus, that inevitably and extremely precisely, sensitive and quick in effect is.

Another object of the invention is to provide an earth drilling method by which the feed ratio of the cutting tool is regulated automatically. This procedure is of great importance in fluid or mud drilling operations as the invention the new feature of inserting the drilling tool makes it practical and easy to be made in accordance with the requirements and limitations imposed by The fluid circulation may be conditioned, like gaseous or water-containing formations subject to processing; The invention also makes it possible to fix

Laser copy

Lumps of clay ο. Like. To prevent the drill or return the drilling tools.

Another object of the invention is to provide an earth drilling method by that maintain a constant pressure on the cutting tool for a substance present can be, despite this pressure automatically in the opposite proportion ίο is changed to the hardness of the fabric that needs to be pierced. That way will the tool advanced at the greatest speed that is compatible with safety lets, and in addition, the various parts of the boring mill are against overload and breakage, as in the case of the hand-controlled drilling rigs used to date Technology entered.

Another object of the invention is to provide a drilling method with a rotatable cutting tool with the help of two driving links and one in between Differential device, whereby a pressure is constantly exerted by the cutting tool, which is a function of the tool weight, modified according to the resistance offered by the formation to be pierced. The objects of the invention also include a system for drilling and putting into action a borehole o. The like. To create, which a minimum amount of investment costs Requires simple and compact design, relatively cheap to build and economical is in operation.

Another object of the invention is a system for producing boreholes to provide with the above-mentioned features, in which an electric driving force general application for the multiple operations involved in drilling and production is made accessible. !

It is still another object of the invention to provide a boring mill that has a Zu- j represents the assembly of compact units that are easily enclosed in a housing that is completed to provide security against damage for the To create workers, and that takes up as little floor space as possible. Another object of the invention is Creation of a speed control system for the drilling rig described, through which under all drilling conditions a certain limit force or contact pressure difference of substantial size is obtained from a changing maximum value.

Another object of the invention is

To provide a simple self-acting means of measuring and displaying the pressure on the cutting edge for all drilling ratios and working depths.

'Another object of the invention is to provide a measuring device, in place of an association of Anzeigeüberbeanspruchungs- and pressure relief elements application, together with a certain new work and a mutual dependency-creating means for _certain: described in detail purposes.

Further objects of the invention will be apparent '■ from the following detailed description ■ in conjunction with the drawings. In these are

Fig. Ι and 2 graphs showing certain characteristics of the electric motors, which in connection with the invention; be turned.

Fig. 3 is a semi-schematic view of an auger rig that is experiencing the new \ * the automatic regulation can apply.

Figure 4 is a detailed plan view of a well drilling rig embodying the invention embodied.

Fig. 5 is a side view thereof.

Fig. 6 is a plan view of the clutch adjustment device used in the system according to Fig. 4 applies.

Figs. 7 and 8 are schematic representations of this, which show the direction in which the coupling levers are to be used for the various processes.

Fig. 9 is a cross-section through a spring member used in the actuating mechanism according to Fig. 6 is used.

Fig. 10 is yet another embodiment of the well drilling rig used for the ram drilling system is suitable, and

Fig. 11 is a side view thereof. Figure 12 is a combined measuring device made in accordance with the present invention.

Fig. 13 is a partly elevational and partly sectional view of the illustration shown in Fig. 12 illustrated apparatus, and Fig. 14 is a schematic representation of a monitoring or control system according to the effect of the illustrated in Fig. 12 Apparatus is able to come into action.

The invention is particularly suitable for the production of oil wells and the like, whereby the intricate circular course of the hand-controlled work during the rotary drilling of a borehole automatically and with a Maximum speed is carried out, which is compatible with the operational safety of the work leaves. In such drilling operations, the work of the drill involves several different ones Circular passages, one of which begins and ends when the circumferential cutting edge just touches the bottom of the borehole,

when the rotating ring, which turns the drill, has come close to the turntable. That means that this circular path is the completion of a distance of about 8 to 15 m of the borehole is equivalent to.

Depending on the earth formations that are hit, this circular path can be several Last hours if it is not interrupted by cutting out some Reason to be changed. The drill will hit both soft and hard material, and with the mode of operation customary in technology up to now, the drill worker had to Drill from time to time after free over-

! 5 advance laying. He had to, with others Words, loosen the brake band from the cable drum, so that the drum is around a short distance Elbow piece could turn, thereby lowering the drill rod and allowing the drill bit took up some of the weight when the bottom of the well was touched. Then the worker pulled the brake band again to hold the drum in place until he thought it was rotating Cut yourself completely or roughly cut free. This cycle must be uninterrupted be repeated when the borehole depth increases.

The pressure on the cutting edge is greatest at the moment when the drum is moving is brought to a standstill again, d. H. when the drill hits the fabric first; it decreases to zero when the drill ■ cuts itself freely. The drill feed, measured for any time or distance, this way is only half of the one who could be achieved if the pressure was consistently on one with security agreed maximum value would be held.

In other words: the automatic feed with such a uniformly regulated one Pressure will advance the tool twice as fast as it would with the best hand control theoretically possible, and in real practical operations there will be all · foresight after this difference must still be considerably larger.

The drill pipe may weigh 20 tons, for example, although only a small part of this weight, e.g. I ¹ Z ₂ -2 tons, should actually be carried by the drill bit, while the remaining weight is carried by the suspension hook. If the specified pressure is exceeded, the cutting edge of the drill bit will very quickly become dull or jagged, and in some cases even more serious effects will occur, e.g. B. bending of the drill string, breaking of the drill or the drill pipe and overexertion of the drilling rig.

When using the method described here, however, all such Prevents malfunctions, as the drill pressure is automatically adjusted according to the pressure to be drilled through Materials, d. H. according to the resistance that the cutting edge of the tool regulates really finds.

Let us first consider Fig. 3 of the drawing; which is illustrated here semi-schematically Apparatus for carrying out the new drilling process has a suitable rotary drill i, which is connected in one of the usual ways to a wind drum device 2, which is controlled by means of a pair of electric motors 3 and 4, between which a suitable differential movement or mechanical coupling 5 to be described below Purposes. The drum device 2 is with the usual hand brake mechanism 6 equipped.

The drill 1 has the usual square or grooved shank 7 for engagement in a turntable or bevel gear 8 and hangs on a pulley system 9 with the help a rope or cable 10 which is carried on the main drum part r 1 of the wind drum device 2 is wound up.

The two electric motors 3 and 4, the first of which is mainly determined by the To generate rotary movement of the drill 1, while the second is suitable, the rule or To carry out surveillance work are to go in opposite directions to one cycle, indicated by arrows, due to a suitable electrical connection a power generator G or another energy source is connected, as described in more detail below is performed.

The drive shaft of the drive motor 3 is in direct connection with a bevel gear 13, which forms the one outer part of the differential device 5. The drive shaft the control motor 4 is also in direct connection with a second Bevel gear 15 shown, which is the other outer part of the differential device forms. The two gears 13 and 15 are for common engagement in an intermediate one or differential member or a bevel gear device 19 suitable; this part lies in the Inside the drum 11 and is attached thereto. The invention is in no way apparent bound by or limited to the use of the differential gear illustrated herein; Rather, other devices can be used to achieve the same effect. The establishment is shown in simplified form in Fig. 3, while the preferred and ready-to-trade Form has found in the illustration to be described later in Fig. 4 to 11.

As mentioned above, the directions of rotation of the two motors 3 and 4 are opposite and are never reversed: the motor 3 is capable of lowering the gear 13 in the Load on the winch drum 2 corresponding direction to lower, while the other Motor 4 drives gear 15 in the direction corresponding to the lifting of the load on the drum. Accordingly, if the two motors 3 and 4 both run essentially synchronously, the speed of the intermediate link becomes, here of the gear 19, be essentially zero, and accordingly the drum part 11 will stand still. This corresponds to the load-free state of the actual boring mill.

If the heavy boring bar is hung over the suspension hook, it naturally arises on the drum part 11 a torque, and as soon as the drill operator applies the braking device 6 solves, the drill 1 begins to go down. The weight of the drill is during this companionway force the drum part 11, the intermediate member 19 of the differential gear 5 to drive, which as a result, a torque through the gear transmission the two electric motors 3 and 4 will exercise. As a result, the engine 3 shown in revolves in a direction corresponding to the downward gear of the drill, driven over-synchronously and act as a power generator. On the other hand, the motor 4 is due to its rotation in the opposite direction of the Work against the differential 5 and act as a motor.

Of course, the speeds of rotation of motors 3 and 4 will be dependent of their special characteristics and also of the gear ratio that is found in the differential 5. For the sake of simplicity it may be assumed that the Motors 3 and 4 are of the same size and have the same speed characteristics, and that they have only to overcome the illustrated burden that has caused is made by the winch drum 2 and the drill 1.

If we disregard the friction in the device, the speed of the motor becomes 3 just as high above the peg as the speed of the motor 4 below the pace. As is known, the speed of the central engagement wheel is 19 of the differential is always equal to half the difference in the running speeds of the Gears 13 and 15 and lies in the same direction as that of the faster running outer wheel. In other words, in the present case, the middle engagement wheel 19 rotate in a direction corresponding to the lowering direction of the drum part 11.

If, for example, the slip of the j control motor 4 is 2 percent under the assumed load conditions, its rotational speed will accordingly be 98 percent of the steady state, while the Mo-! tor will run 3 with 102 ProzentderGleichgangsgeschwindigkeit, as represented by the curve leaves (Fig. ι and 2) is illustrated the relationships of the percentage of synchronizing speed and the percentage borrowed the full load of the motors 3 and 4 illus- under the various working conditions ■. The difference in motor speeds, divided by 2, gives the working speed of the central gear part 19 and the cable drum 11, taking into account the gear ratios Depending on the increase in the depth of the borehole.

The regulating motor 4 thus removes energy under the assumed conditions 'the supply circuit while the other! Motor 3 as a power generator as a result of its drive supplies energy to the supply circuit beyond the synchronous speed. Apart from the comparatively small ver! the two motors keep each other in this way

essential the balance, and the kine-; table energy of the opposite of the drum member 11 moving load is only used: to lower the load itself. if ; the engine 3 has other work than engine; performs, e.g. B. when he drives the turntable 8, so will the force exerted by the windmill; drum 2 is generated, in this way the ] Help Motor 3 do that work.

The work of the regulating motor 4 always consists in the fact that it digs the drill out of the borehole or seeks to dig it out. This statement applies to all times, including the periods when the drill actually goes down. The load on the motor 4 is equal to the torque which is generated by the drum 11 multiplied by the speed which, according to its speed ^curve: and the gear ratio, would be imposed on the drum part 11 if the other motor 3 were at a standstill. Since the torque on the drum member 11 is generated by the attached load of the drill ι, it follows that the load on the motor 4 is always an exact measure of that weight, as will be explained in detail below.

The moving element that is probably best used in the new control method is suitable, the well-known induction motor, because even comparatively small changes its torque translates into changes in running speed almost instantaneously

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reflect, whereby the movements of the drill ι easily and instantly mastered can be.

A circular course of the drilling work corresponding to the length of the drill rod will now be described. When the drill goes downwards and the drilling tool is not yet in contact with the bottom of the borehole the weight on the hook is greatest,

ίο. and the load on motor 4 is for that particular one Circular walk a maximum. As a result, the speed of the motor 4 is for it Circular walk then the least.

The motor 4 is, as previously stated, with more than steady speed as a result of the Down gear of the drill rod driven. But even now it drives the turntable. That requires force even though the boring tool is not yet cutting, so the real load on motor 3 is always the resultant of the negative load caused by the drum part 11 is generated, and from the positive load caused by the rotary table 8. These resulting load is smallest when the rotating drill goes down and not yet j has started to cut. Accordingly, the running speed of the motor 3 is then for this circle is the largest.

The slower the speed of the motor 4, the faster the middle one runs Toothed gear 19, and the greater the speed of the motor 3, the greater the of the gear part 19, so that when the drill is down, while it is not yet cutting det, we find the state of the greatest difference in the speeds of motors 4 and 3 have, d. H. the maximum movement ratio of the drum part 11 and the drill 1. Thus is used for a given weight of the drill pipe and certain engine characteristics this ratio of free movement is not exceeded under the drilling conditions, and the Feed for each revolution of the rotating tool can be in the desired manner be limited.

It is now assumed that the cutting edge of the drill touches the ground. Part of the weight of the drill pipe is then carried by the cutting edge striking the bottom of the hole and the weight on the hook is reduced by exactly this part. The load on the control motor 4 is exactly in proportion to Reduced pressure on the cutting edge of the drill. Decreasing the load reduces the slip of the motor, so that the motor 4 now faster, and the intermediate gear 19 runs more slowly; d. H. the movement of the drum part 11 and the feed of the drill 1 is slower.

When the drill begins to cut, the load on the motor 3 increases in proportion the diameter of the \ {3 ear crown and the pressure on the cutting edge. Increasing the burden increases hatching; accordingly, the motor 3 runs more slowly. As a result, turns the differential part 19 and in the same way the drum part 11 more slowly.

Thus, the feed of the drill starts to decrease due to the mutual work of the motors 3 and 4. When it decreases, the reverse occurs; the pressure on the cutting edge decreases, the weight on the hook increases, the load on the control motor 4 increases, the speed of the motor 4 decreases. In the same way, the decrease in the cutting pressure decreases the resistance of the cutting tool, the load on the motor 3 decreases and its speed increases. In this case, the two motors 3 and 4 cause the differential member 19 and the drum 11 to run faster.

At any point between the maximum feed and the zero feed, there is an offset reached, and the feed will become even for a given fabric. That The feed ratio depends on the resistance that the material to be drilled through offers the tool, but this resistance is determined by the pressure on the tool cutting edge, which is again proportional to the load on the hook of the load on the motor 4 and its speed.

When the cutting edge of the drill touches the hardest rock, we have the outermost one Limit of zero resistance on the drill as it approaches and the maximum resistance at the touch. Obviously, for a given pressure, the slowest advance will occur through this hardest material. The advance through all other substances will take place more quickly, and in reverse Relation to their resistance. In particular is the ratio of the longitudinal feed the cutting tool, d. H. the degree of penetration by clay so regulated, that the cutting chips are very thin cuts, which the circulating rinse water easily dissolves, so that lump formation is avoided. As stated above, an equal no Maintains moderate pressure on the drill when piercing a particular fabric, d. H. the maximum feed ratio is achieved. If then the one to be agreed with the security Maximum pressure on the drill edge for the hardest rock set as the pressure limit the feed ratio of the cutting edge for all other materials that can be pierced, for example, must remain within the safety limit. iao

As stated above, it is well known that when the two cone

wheels 13 and 15 in opposite directions the middle part 19 rotates with half the difference between their speed and in the direction of greater speed.

With regard to the drive motor and the control motor4 Accordingly, the speed relations can be expressed by the equation will

so equation IV assumes other values: these may be expressed through

I. 2

where Z “is the speed of the motor 3, Z _{c is} the speed of the motor 4 and Z is the speed of the intermediate member 19.

When the intermediate member 19 with the drum 11 is connected by a toothed gear or a member replacing it, equation becomes I to

II [Z ₁₁ - Z,) / C = Z ₁ , or TTT 7 7 c

where K ^{1 means} Zo of the gear ratio and is constant and

^ - _K ■

When S _{d is} positive it can be seen that the movement of the drum 11 lies in the direction of the motor 3, ie in the lowering direction. When S _{d is} negative, the drum 11 moves in the direction of the motor 4, that is, in the stroke direction.

It is also well known that the speeds of induction motors are frequent are specified in hatching ratios or as a difference from synchronous gear, and that the torque of such a motor is essentially proportional changes to its hatching. Then equation III becomes j

JY $ $ __. £ ■ ι

where S ₁ . the slip of the motor 4 and S _a , the slip of the motor 3 means. ;

When the motor 3 ^j exceeds the Gleichgangsgeschwin- (ligkeit, its slippage is negative, and Equation IV takes the form

V S _c -f- S _a = S _d . ;

Apparently, S _d can only change when the torque or the engine characteristics change. \

The equation V illustrates the loading \ dingung when the drill freely downwards

moved or just slightly on the sides ^!

cuts but not on the bottom of the hole j

rests. The equation thus gives the maxi;

ratio of the drill feed rate. '' Is the bit on the ground, VI

• S _0x = S,

dx>

therein S _{cx means} the slip of the motor 4 as a result of its reduced torque, S _11x the slip of the motor 3 as a result of the load on the drilling tool during cutting, S _cx the value S _c reduced by the slip value caused by what is now resting on the ground Drilling weight.

In equation V, S _{a is} caused by: the tensile force due to the downward movement of the drill rod. Accordingly, when the tool cuts on the ground, it first makes use of the tensile force represented by S ₁₁ , and then the moment represented by S _ax. The torque on the drill rod is then proportional to the value S _ax + S _a .

If S ₁₁ = S _cx , then equation VI: S _11x ^ O. That is, the rotational load due to the cutting of the drill can be restricted to a value which can be easily determined and controlled in advance.
The relationship

ex ax dx ■

can only apply for an infinitely small period of time. This result follows that, since S _{cx is} smaller than S _c , the drilling tool! ^au f pushes the ground and cuts. Thus, there must be a balancing relationship such that S _cx - S _ax = S _dx equals any positive value, even if it is small, and the drill will move down smoothly. That is, S _{11x can} never be equal to S _cx except that a load other than cutting work is imposed on the motor 3. This condition could occur with rubble 0, the like; but it can be seen that only a small increase in the torque of the motor 4 will actually bring the value S _dx to zero and even to a negative value, which means that an upward movement of the drill occurs.

Thus, the regulation is necessarily precisely sensitive and extremely fast, and difficulties such as over-turning, breakage, overexertion, jamming of the drill, overloading and the like are prevented.

In Fig. 4 to 11 the preferred one is used mechanical design of the system or a complete arrangement of the parts to make the above usable Monitoring procedure, illustrated.

The earth drilling takes place preferably after the system of rotary drilling and after the impact drill instead of and sometimes with the union of the two.

In rotary drilling, it is common to use a

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to arrange complete power and drilling system on the crane floor, nothing of which for the shock system and can be made usable for the production work. It required separate and special foundations, beams and containment parts for the associated ones Components, so that after completion of the rotary drilling, the entire machinery of the floor must be removed while the ίο foundation supports and housings for the following Lifting and fountain operations cannot be used.

This also applies more or less to the impact system. Much of the apparatus used in this drilling system remains with the crane and is used as part of the generating plant. However, it is necessary to have the machine or motor replaced by a _; - to replace others with different capabilities and to change some parts of the drive and speed change mechanism.

In this way, three different power plants are created in a combined system used for turning, butt drilling and manufacturing work. The totality these power sets by far exceed the maximum power requirement of each of the individual Investments. There was also a duplication of winches, countershafts and others Parts for the same tasks in the three jobs of rotary and butt drilling and the Promotion work takes place.

In ordinary rotary drilling, the aim was the size and weight of the rig so that it was able to withstand the violent bumps and vibrations that with such drilling rigs are inevitable to withstand and they to a certain extent Degrees to be consumed.

The control procedure described above particularly avoids the need heavy types of apparatus, all the more since the regulation of the drilling is so perfected, that the irregularities of the drilling work are compensated, and that in the used System can be expected with a normal load factor. In the application of the method of drilling wells, it is possible to use smaller power plants, which are particularly suitable for the various additional devices associated therewith put into action, and which is applied as a total system for the work that require the maximum available force, such as. B. the fast lever o. The like. Accordingly, the unit the engine capacity is a minimum for the proper execution of the work, and it is economical, not only in investment costs, but also highly effective in terms of the 'load factor, the force factor and the : Operating cost.

The invention is directed to an electrical universal well drilling rig in which j a plurality of motors, countershafts, transmission and differential gear sets are located, which are coupled by a suitable power transmission system so that they independently of each other the lathe, the various hoists, winches, slurry pumps and able to drive the balancer. The transmission is designed in such a way that it makes it possible to control the motors in this way couple so that their total power can be used to operate the winches. That Movement is arranged so that the system without changing the space, the engine and of the lifting devices on the crane, apart from the removal of the parts, which are necessary in the following Work stages are not needed, is able to do the following work depending to perform one or more: rotary drilling, push drilling, combined rotary and push drilling, Pumping (when making), drawing up and cleaning (when making).

Since only one set of foundations, girders and casing is necessary, the crane cost is and the floor space is considerably less than in the older systems. -

In rotary drilling, the extremely heavy weights that are necessary and the demands of working on more or less distant drilling fields. Friction clutches with the possibility of slipping in critical moments. Therefore, the rotating links are generally inevitable Claw couplings in use. As is well known, the coupling parts must be brought into synchronization in order to interlock to intervene or be disengaged when rotation is just beginning, ceases or reverses. If there is an adjustment even at very low rotational speeds If an attempt is made, the result is severe shock and shock, which often leads to injuries the worker and break in the transmission leads.

One of the objects of the invention is to provide for avoiding these difficulties of springs in the coupling linkage and by suitable interlocking of the various Clutch and brake parts, which can be done both mechanically and electrically.

The lathe is usually driven by a chain from a main shaft, which is arranged so that the chain allows freedom of movement for workers and materials obstructed on one side of the crane, and such a drive often has damage the worker led.

The invention eliminates these deficiencies

by placing the chain close to the ground and suitably encapsulating it.

As can be seen from Fig. 4, the well drilling rig has in particular one rotatable drilling table 101, a wind or lifting device 102, a main drive motor 103, an associated variable speed motor 104 driven by the differential gear train 105 is coupled, a plurality of sludge pumps 106, a pump countershaft 107, which can be coupled to the pumps, a motor 108 for driving the pump shaft 107, a gear reduction gear 109 connected to the main drive shaft 110 of the differential set 105 and the Pump shaft 107 can be connected in, a hand wheel, a crane 112 and a main post 113.

The rotatable drill is mounted in an opening 115 of the drill table 101, which passes through a bevel gear 116 is connected to the drive shaft 117, whereupon a chain: wheel 118 is appropriately positioned; a removable two-piece sprocket 119 on the main drive shaft no. The sprockets 118 and 119 are supported by a chain 120 in connection through which the rotary drill is driven. The winch 102 is with equipped with a cable feed drum 121, which has the task of carrying the drill pipe, which is attached to a steel cable, not shown, and via the usual pulley runs and is wound on the drum to feed; forms the mentioned drum the main winch drum for quick lifting of the drill casing and the like.

The drum 121 is indirectly connected to the main drive shaft 110 by the reduction gear 109 via a chain wheel drive 122, to which a chain wheel 123 belongs, which is attached directly to the cross 124 of the drum. This drive completely eliminates the torsional stresses that occurred with the earlier types of drum shafts * 5 and allows the drum part to be made lighter. In earlier j rotary drilling rigs, the drum 121 was connected to the drive by a reduction gear; part connected; but this is not necessary if a differential gear is used, through which the speed of the drill feed is regulated evenly. A shaft 126 with a pair of cranks 127. The drum 121 is supported at both ends near the ' drum 121 and is provided with a sprocket 128 in line with the sprocket 129 on the pump shaft 107, to which it is connected by a chain 130.

The main drive set contains a motor 103 for two speeds and a variable speed motor 104, which by flexible couplings 135 are connected to the differential 105, and forms part of the permanent system, which is used for all drilling and production work. These units can be on a permanent foundation be applied, as it is, for example, the cover plate 125 (Fig. 5).

The differential consists of a pair of spur gears 136 and 137 that connect to the bevel gears 138, 139 consist of one piece or are attached thereto, and which are mounted on a sleeve 140 or on the main drive shaft 110 that passes through it. The wheels 136, 137 are in engagement with the pinions 141 and 142 on waves 143 and 144, which are stored in the gear box or housing 145. A set of planet gears

146 sits on a hub 147 which is on the shaft 110 is keyed and part of the differential gear forms. At the end of the shaft 110 there is a coupling 148 to the main shaft 110 to couple with the transmission 136 and thereby simultaneously the wheels 139, 136, 138 and

147 to be connected to the shaft 110. Further

a stop pin, not shown, is provided and retained on gear box 145 to lock one side of the differential to change the speed ratio if required.

The split sprocket 119 is freely rotatably arranged on the shaft 110; it owns one Side spiral dome claws 150, which are able to click on appropriately designed claws one to act movable coupling part 151, and the opposite side of the sprocket 119 has square coupling claws and angular coupling claws 152 equipped, which can cooperate with the clutch 153. The main drive shaft 110 is rotatably mounted in the housing 145 as well in a stator support bearing 154. The countershaft 107 for the mud pumps is in suitable Support bearings 155 supported and has a roller 156, sprocket gear 129 and a sprocket 157, which is mounted on the extended hub portion 158 of a spiral coupling 159 is. At the opposite end, the shaft 107 is equipped with a spiral coupling 160, which is able to act on a free shaft 161 which rests in the stator bearings 155 and carries a pulley 162 for belt connection with pulleys 163 of the mud pump 106 to create. The roller 156 lies in a plane with the drive roller 165 and is on the motor 108 is connected by an unillustrated belt.

The reduction gear set 109 has a gear box or housing 166 with a pair of shafts 167 and 168 mounted therein, the ends of which protrude through the Stand block bearing 155 are carried. A plurality of end bearings 169 to 172 are on

the shafts 167, 168 mounted. The wheel 169, which can rotate on the shaft 167 is with an extension sleeve 173, with a spiral coupling 170 equipped, which is able to act on the hub 175 of the sprocket 176, which can rotate freely on shaft 177. The opposite side of the wheel 176 can cooperate with the square claw coupling 177, which is keyed onto the shaft 167 is. On shaft 168 outside of gear box 166 are a pair of sprockets 178, 179 attached; these wheels are connected to the sprockets by chains 181 and 182 180 and 157 in connection.

A handwheel gearbox in consists of a crankshaft 184 with a mounted thereon grooved wheel 185, which in connection with a drive wheel 186 (Fig. 10 and 11) for the Rotate the suspended tool

ao can. The shaft 184 is in communication with the main drive shaft 110 through a sprocket 187.

As shown in Fig. 6, the engaging coupling parts are through a system of Actuators connected to levers 210-212 located in a suitable corner of crane 112 are housed. The levers sit on shafts 213 and work on grooved segments 214. The lever 210 is connected to an adjusting rod 216 by a spring member 215, which has a pair of tenon yokes 217, attached to act on clutches 174 and 177. Of the Lever 211 can activate clutches 148, 159 and 160 in the same way, and lever 2i2 clutches i5i and 153. The spring members 215 (Fig. 6 and 9) consist of a tubular housing 218 with Plugs 219 having an opening 220 capable of receiving rods 216; these are with stop nuts 221, movable neck rings 222 and lock nuts 223 equipped. Between the plugs 219 and the collars 222 are coil springs 224 equipped; these are brought into such a preload by adjusting the nuts 223, that they secure the neutral position of the couplings. One arranged in the housing 218 Tube 225 is movably connected thereto by a pin 226 which is' in the longitudinal grooves 227 can slide.

When the shift levers are operated, the tubes 225 are against the collars 222 printed, which the rods 216 over the springs 224, creating a resilient connection between the control levers and the Couplings is created.

To reverse the couplings, the levers are swiveled to the opposite side, and the pins 226 move the housings 218 against the springs 225, whereby the j rods 216 are operated in the opposite direction.

The operation of the device is short; following: The drilling work is done by the engines 103 and 104 through the differential 105 ■ and the main drive shaft no through a chain ! connection 120 to the rotary drive shaft 117 bej works. As described above, the J motors and the differential regulate the feed rate of the drill according to the resistance that the drilling tool finds in the various soil formations. Of the The drill is fed automatically via the drum 102 through its connection with the Shaft regulated via the reduction gear 109. In the 'drilling work are the sprockets 119 and 176 with the spiral claw clutches 151 and 174 engaged. The drilling table 101 and the feed drum 121 become both through the differential 105 from the drive motor 103 and the variable-speed motor assigned to it 104 brought into effect.

The pumps 106 are driven simultaneously by the countershaft 107 by the motor 108 driven when the screw coupling 160 is engaged.

When the drum 121 is used for lifting purposes is, the spiral dog clutches 151, 160 and 174 are disengaged. the Claw clutches 159 and 177 are engaged to motors 103, 104 and 108 through the transmission gears 171 and 172 and the chain τ 22 with the drum 121 to coupling, whereby all available force is used for lifting at high speed will.

The differential and an engine control, not shown, are arranged to, as described above, different running speeds for the drive shaft iid and that Windwork 102 to create.

Fig. 7 and 8 schematically indicate the direction in which the levers are adjusted for the drilling process (Fig. 7) and the quick lifting process (Fig. 8). The arrows illustrate the levers, and drilling is 210 on the left groove of the segment 214 set, lever 211 also on j the left and lever 212 on the right groove. For lifting, lever 210 is set to the right, 211 to the right and 212 to a neutral position. The couplings are therefore for the purposes and in accordance with the description above set for the operation of the mechanism. It is possible other than those shown still achieve different running combinations with the signal box, and it can be seen that the spring members shocks or impact effects, which occurred in the earlier apparatus found, prevent.

The above description of the

IO

Finding is intended to illustrate the alignment of the universal electric drive, which is used for the rotary boring mill is necessary, but the apparatus is also applicable to cable tool drilling and can be used as a combination system for rotary and cable boring mills. As illustrated in fig. Io and xi is, by adding the drive wheel 186 and the balancer 190, which can be oscillated in the Main post 113 is mounted, the system is set up for drilling by means of Kabehverkzeuges and the reduction gear 109, which is not part of the permanent system, can be underneath the wind drum 102 to which it is connected. The driving wheel 186 is in the usual way in connection with a cable drive 199. The pump motor 108, usually is of greater capacity than the main drive motors 103 and 104, can Step in place of the motor 104 in order to achieve a greater efficiency for the work of the cable tool to obtain.

The pumps 106 and the countershaft 107 are removed for this drilling. The main drive shaft 11 ο is connected by a 200 in. Chain Connection to the sprocket 187 of the handwheel 185. The crankshaft 126 is through a Chain drive 201 with the drive shaft 110 in connection. The balancer guides its oscillation around a joint 202 on the column 113 with the aid a connecting rod 203 articulated to the crankshaft 184 and the other End works in conjunction with a relief screw 204.

After completion of the drilling work, the motor 103, its control devices and leave the differential gear set in its original position for eventual production work, pumping and the like. The remaining Motors, control devices and the reduction gear set are removed.

It can be seen from the foregoing description that the proposed Apparatus for drilling boreholes using both the rotary and the cable tool method is applicable, and that it approximately or completely meets all the requirements for a compulsory and appropriate regulation and with regard to the accessibility of the parts. It facilitates the arrangements and The unification of the mechanism for the various processes substantially reduces the Production costs, creates safety for the operating team and allows a working speed, which was inaccessible with the earlier devices.

It should now focus on the

Apparatus for automatically limiting the

Drilling pressure and for measuring the changing Values of pressure can be addressed during work.

In Fig. 12 illustrates the illustrated ^; Set up a suitable housing 301, on ^! to which a support part 302 is attached in a suitable manner; which has a pair of arms 303 arranged at an angle and preferably made in one piece therewith. The support part 302 is capable of supporting a part of the movable measuring members, as will be described in detail below.

The measuring device is provided with a suitable one Glass front 304 equipped to close the usual opening in the housing part 301. A fixed washer part 305 is mounted in the housing closely behind the glass surface 304, while a movable disk or maximum demand segment 306 that is semicircular may be designed, firmly seated on a sleeve 307 which goes up through the glass plate 304 and the support part · 302 passes through and terminates in a button or the like 308, by means of which segment 306 can be shifted or adjusted by hand.

A second movable or compression limit disk 309 of circular shape is below the movable segment 306 and substantially in lateral alignment with the stationary one Disk 305 arranged. A centrally located pin or shaft 310 is fixed connected to the movable disc 309 and passes up through the sleeve 307; at the At the end there is a button or the like 311, which is located above the larger button 308. As a result, the movable disk 309 can also be adjusted manually by means of the button 311 will; but under normal working conditions the disk 309 moves with the segment 306 as a result of the interposition a friction band or ring 307 "inside the sleeve 307 so that the Shaft 310 is taken along in a suitable manner.

A single phase wattmeter element 312 is in housing 301 below the various disk members arranged, which has a display arm 313 for a below described in detail Able to adjust the monitoring task. A combined driving and braking mechanism 314 for the movable segment 306. which is preferably of the usual clockwork design is also housed in the housing 301. The wattmeter portion 312 can be from be of any known shape and essentially include a tension coil 316, which is wound on a suitable pole projection 317 and a current coil 318 a pair of suitable pole protrusions 319. all of the pole protrusions in the conventional magnetic Circles are arranged. A rotatable disk 320 can by the interaction of the flux of lines of force from the various Pole protrusions are put into action

the; it is firmly connected to a spindle 321 on which the arm 313 is seated. The spindle 321 is suitably stored in the housing 301 and is provided with a coil spring 322 in the usual manner.

The display arm 313 is rectangular in shape and its outer end is flat Pointer 323 is provided to which a suitable, U-shaped contact part 324 is attached is. This contact part can either act on the contact segment 325, which is on the lower side of segment 306 for the maximum requirement, or on the contact segment 326, which is attached to the top of the pressure limiting disk 309, depending on the working position that the pointer 313 according to the following explanation. Movable "segment 306 is also shown a contact member 327 for acting on a ^ fixed contact member 328 in the zero or Switch-off position of segment 306! see; the purpose of this arrangement is given below j explained on the basis of Fig. 14. j

The clockwork mechanism 314 has a suitable base plate part 330 for carrying! a brake coil 331 and a movable brake arm 332 which is supported by a suitable; Coil spring 333 according to the illustrated; Position is pulled. The free end of the \ brake arm 332 is provided with a resilient _: brake shoe 334 for acting on a climbing; wheel 335 0. Like. A suitable clockwork 336 'is provided. In the illustrated state of de-energization of the brake coil 331, the brake arm is withdrawn from the climbing wheel 335; As a result, the clockwork 336 can rotate a pinion 337 which is in engagement with the gear toothed outer surface of the movable segment 'is ment 306th t

The pointer 313 is suitable on the fixed plate 306 the instantaneous Display drilling pressure, as explained below, while moving segment 306 | j corresponds to a maximum requirement element and is set to be full weight corresponds to the rotary drilling device. The movable disk 309 corresponds to the tallest Cutting edge pressure, the application of which is desired; she can also. so set as it corresponds to the drilling conditions j. j

It is now the Fig. 14 considered, in 'which the control system shown the; various coils and contact parts' of the: measuring device, which in Fig. 12 j and 13 and a three phase power source 340 for feeding a plurality of induction motors 338 and 341, which correspond to the table drive motor and the auxiliary or control motor, which according to! According to the effective weight of the boring mill j are fed with energy, which in the prescribed system is used.

A suitable self-starter or the like 342 is used to connect the motors 338 and 341 to the power source 340 under working conditions by means of an induction regulator 343. This regulator includes a fixed primary winding 344 of any suitable type and a plurality of rotatable secondary windings 339 and 345 which are connected to the circuit of the primary windings of induction motors 338 and 341, respectively. The secondary parts 339 and 345 can be driven through the intermediary of a common shaft 343 ^a , which is suitably connected to a control motor or the like 346, which is attached to the top of the induction regulator. The corresponding windings of the two rotatable elements 339 and 345! of the induction regulator are in any case, as shown, wound so that they are 180 electrical degrees out of phase with each other. In addition, one of these secondary members is initially in its position of maximum amplification of the supplied voltage, while the other at the same time assumes its position of maximum decrease in the supplied voltage. As a result, a small movement of the control motor 346 seeks to increase the voltage which is supplied to one of the induction motors 338 and 341, while at the same time the voltage for the other motor is reduced. In this way, a very sensitive control is ensured to the extent that a comparatively large change in the running speed of the induction motors is obtained by means of a comparatively small movement of the control motor 346. It is clear that other means, e.g. B. separate runners, which are forced by gear engagement to skid in opposite directions, are used to ensure the duplex regulation that is required, and that the arrangement shown is merely an illustration, for example.

To excite the control motor 346 via a drum switch 348 and an overload currentless relay 349 is a second power source, preferably a three-wire DC power source 347, provided. The drum switch 348 may have a suitable drum portion 351 the appropriate control finger or contact segments are attached, as in the following in is described individually. For the purpose of adjusting the drum switch in one or other of his working positions from the middle position shown serves a pair of Working solenoids 353 and 354, \ yelche the drum in different directions to adjust; instead, a

any substitute device can be used for the same goal.

The relay 34g may have a work coil 356 and a plurality of movable switching arms 357. 358 own. The arm 357 is normal after the Open position directed so that it makes contact with a pair of fixed contact parts 359 interrupts, while the other switching arm 358 is directed normally so that it is on a ίο a pair of fixed contact members 360 acts. The contact parts 359 and 360 are connected in series, so that an open circuit in connection with each pair of contact members the following circuit of the Control motor 346 interrupts.

If an overload current flows, the switch arm 358 is actuated by the coil 356 so that that he releases the contact members 360, while in the state of no current the De-energizing the coil 356 enables the arm 357 to go into the open position. Of the The apparatus just described thus acts at the same time as an overcurrent protection device and also as a No-load fuse.

A small voltage converter 361, which is in Bridge is connected to a phase of the auxiliary induction motor 341, is able to excite the voltage coil 316 of the measuring apparatus shown and also to provide energy for other control circles to be followed. A small Stromumformer362, which according to of the primary current of the auxiliary induction motor 341 is excited, is through the work coil 356 of the overload relay 349 and connected by the current coil 318 of the illustrated measuring device.

As explained above, the motor 338 can directly operate the turntable for the Drill to drive while the auxiliary motor 341 so through the intermediary of a differential gear coupled and is always fed according to the size of the effective weight, which has the attached drilling member.

The current coil 318 of the measuring device is energized in accordance with the primary current of the induction motor 341 and the voltage coil 316 is energized in accordance with the voltage applied to the primary winding of this motor. The display arm 313 of the measuring device thus adjusts itself in accordance with the usual operation of a single-phase wattmeter. The movable segment 306, as mentioned above, corresponds to a maximum demand measuring device and is arranged in the present example so that it can be moved forward from the automatic pointer 313 by switching on the clockwork device 314, for the purpose of the mechanical work of actuating the maximum demand segment 306 the pointer 313 are not immediately imposed, whereby due to friction or un-; Sufficient torque on the pointer arm: inaccuracies could arise. The maximum demand segment therefore always shows a value corresponding to the maximum torque which the auxiliary induction motor 341 requires during work. The extreme value of this torque is relatively equal to \ the full weight of the attached drilling; Element. Since the drill pipe is elongated during the drilling work, or since the weight increases due to the fact that the drill cable is unwound from the drum, the maximum demand segment 306 will automatically be advanced by the action of the clock mechanism 316 as soon as the contact part 324 is at Pointer arm 313 and the contact portion 13, 325 of movable segment 306: come into engagement, as will be described in detail below.

As soon as the bit hits the bottom of the borehole, the effective weight is reduced by the full contact pressure if a single rope is used for suspension purposes, and is reduced by the contact pressure increased by the number of rope strands when a block and tackle has two or more ropes . It is used when the depth of the borehole increases and additional pieces of pipe are added to the drilling part. In order to suitably correspond to the different numbers of rope strands, or to make an adjustment according to the different, previously determined limits of the contact pressure, the pressure limiting disk 309 can be brought into the desired angular position relative to the maximum requirement segment 306 by hand using the adjusting knob 311.

Under the working conditions just described, the actuating indicator arm 313 move backwards from the maximum demand segment 306 or in other words: the effective weight of the regulating element is equal to its attached maximum weight, reduced by the contact pressure divided by the number of strands in the pulley. Consequently the measuring instrument is always exactly the pressure on the drill bit divided by the Measure the number of ropes in the pulley system, and if the scales are suitably calibrated, as in Fig. 12 displayed, immediate readings of the contact pressures can also be obtained. Consequently is a simple, automatic means of measuring and displaying the pressure on the Drill cutting edge created for all drilling conditions and drilling depths.

Assume that the indicator arm 313 moves in the clockwise direction until its contact part 324 contacts contact portion 325 on maximum demand segment 306; it then becomes a Circuit closed from the one terminal of the auxiliary transducer 361 via the

B851B1

Conductor 365, contact part 360 and 359 of relay 349, pointer arm 313, contact parts 324 and 325 (which are now in contact), the brake coil 331 of the movement 314 and from here to the other terminal of the auxiliary converter 361 leads. In this circuit, the brake coil 331 is excited and pulls the brake part 334 from climbing wheel 335. The clockwork device 336 consequently drives the maximum demand segment 306 by means of the pinion 3.37 as long as the indicator arm continues to move to the right until a symbol according to the maximum weight of the drilling part is reached, provided that the process is so far to be led. The decrease in torque on pointer arm 313 causes separation of contacts 324 and 325, whereby the brake coil 331 is de-energized and the brake 334 again is stimulated. The maximum segment 306 becomes

ao come to a standstill in this way while the display arm 313 is free to move can.

The movable disk 309, which corresponds to the limitation of the permissible pressure at the drill bit, is, as described above, in frictional connection with the maximum requirement segment 306, so that the disk 309 is always carried along directly by the segment 306 in order to maintain a constant difference or a Maintain an employment ratio of a substantial magnitude with respect to the changing maximum value as indicated by segment 306. However, as described above, the setting of the movable disk 309 can be carried out by hand with respect to the segment 306 in order to adapt it to the particular drilling conditions. Assume that movable disc 309 is angularly positioned relative to maximum demand segment 306 corresponding to the relative positions of contacts 325 and 326 in Figure 14, and that arm 313 of segment 306 moves backward until the pressure limit has been reached which corresponds to a meeting of the contact segment 324 on the pointer arm 313 and contact segment 326 on the movable disk 309; then an auxiliary circuit is established from auxiliary converter 361 via relay 349 and arm 313, contacts 324 and 326, conductor 366, working winding 353 of drum switch 348 and conductor 367 to the other side of converter 361. The drum switch 348 is thereby moved into its right position α .

Thereafter, a circuit is made from the positive pole of DC power source 347 via conductors 368, field winding 369 of the control motor 346 to branch point 370 produced by where the stream divides. A branch leads over

the contact segment 371 of the drum switch 348, which has a pair of control fingers on this bridged, and the neutral 372 of the; Three-wire source 347. The second branch leads via the armature 373, contact segment 374 of the drum switch 348, which is also a pair j control finger bridged on this, and to the negative conductor 375 of the power source 344 ..

With this simultaneous excitation of the armature and the field winding of the control motor

346, the induction regulator 343 is operated so that it is simultaneously and in opposite Meaning changes the voltages applied to the main drive motor 338 and the auxiliary or regulating motor 341 as described above.

Since the indications of the pointer 313 are proportional to the contact pressure by the number of cables in Pulley blocks are, as explained above, so it follows that when the drill man determines the drilling diameter or changes the number of cables, he should then adjust the movable pulley 309 again according to the Pressure limit. The present device is capable of the return of the induction regulator 343 to its initial or starting position every time the drill worker readjusts the pressure relief disk 309.

This result is brought about by a movement of the maximum demand segment 306 into its zero position with the aid of the button 308, whereby the contacts 327 and 328 are brought to act on one another. Here, a circuit is established from one terminal of the auxiliary converter 361 through the contacts 328 and 327, the switching coil 354 of the drum switch 348 and from here through the conductor 367 to the other terminal of the converter 361. The drum switch 348 is brought to its position b in this way.

This creates a new circuit from the positive pole of the energy source 347 via conductors 368, field magnet 369 in the same direction as previously described, branch point 370, Contact segment 376 bridged by a pair of control fingers of drum switch 348 and the neutral conductor 372 of the power source 347 is closed. A second circuit is produced by the positive pole of the source

347 via conductor 377, contact segment 378 of drum 348 (which is through a pair of control fingers is bridged) and from here by the armature 373 of the control motor 346, opposite the previous direction of the current to branch point 370, from where the circuit proceeds in the manner described above continues.

As a result, the induction regulator 343 is automatically returned to its starting position, what the maximum increase in voltage for one of the induction motors and the Corresponds to the maximum decrease in voltage for the other as soon as the maximum demand

885131

segment 306 is brought into the zero position. After the operation, the drill worker can in the previously described way its pressure limiting parts 309 in the required new position bring.

A very flexible and effective control method can be seen in this way created, which is particularly suitable for any type of earth drilling or the like. at them Cutting tools work on or in different materials. This control procedure automatically changes the feed ratio of the cutting tool as required of the cut material and maintains the maximum feed ratio that corresponds to Security is permissible. By using this invention it is achieved that the drill man does not have to personally endeavor to relieve the pressure on feeling, face or hearing to lay the cutting edges and their process. Instead, he just needs that necessary electrical switch to close, whereupon the device automatically over the the entire length of the drill rod will work, and the drill worker can during this time unhindered to turn his attention to other work.

Thus, in other words, it can be shown that most of the so-called accidents and "unavoidable disturbances" when drilling, of which one can find in the relevant, Technique prior to the present invention spoke | only learn from the imperfect \ 'the J Manual control stick, while the invention i automatically the occurrence of such accidents j and avoids disturbances by the fact that it j drilling process according to the measure to be carried out ' drilling material regulates.

The invention is not limited to the particular structural details, circuits or arrangements limited by parts that were described above, since various amendments j genes can be made without thereby j being out of the spirit and scope of the invention dung is softened.

Claims (6)

Patent Claims: ι. Procedure for regulating the drilling head in earth drilling rigs, characterized in that two motors are provided which are driven by a differential gear device are in connection with each other, and one of which is used to regulate the mold pressure against that of j serves for drilling good, while the other j is used to drive the drilling tool, such that the pressure of the drilling tool constantly behaves the same Hardness or resistance of the material to be cut. 2. Earth drilling rig for carrying out the method according to claim 1, in which a plurality of motors are used to drive the drilling tool, its contact pressure to regulate, to drive circulation pumps and to operate windmills, characterized in that the various, motor-driven devices through gear shafts and coupling treatment devices are brought into connection in such a way that all motors simultaneously to act on the Windwork can be brought. 3. Earth drilling rig for the execution of the λ experienced according to claim 1 with 'an electric motor for advancing the drilling tool and for regulating its contact pressure, characterized in that a regulating device for setting the Power supply to the motor is controlled by a wattmeter relay, the movable part (320) of the wattmeter, the has a movable contact (323) in accordance with the pressure on the drilling tool is operated. 4. Control device according to claim 3, characterized in that contacts (325,326), which interact with the movable contact (323) of the wattmeter, as long as the pressure on the drilling tool is zero, to the maximum demand to indicate power on the electric motor to advance the tool and at the same time to allow the motor to Continue advancing the tool until the desired pressure is reached between the tool and the rock to be drilled. 5. Control device according to claim 4 for the production of vertical boreholes, characterized in that the contact (326) for limiting the pressure of the drilling tool by hand as required the changes in the weight of the tool and the means carrying it with the Increase in the borehole depth is adjustable. 6. Control device according to claim 3, characterized in that a contact (325) to indicate the maximum demand from the movable contact (323) of the wattmeter is removed by a clockwork (314) operated by an electric brake (334) is stopped as soon as the increase in demand ceases. For this purpose 2 sheets of drawings.