EP2514911B1 - Drilling device - Google Patents

Drilling device Download PDF

Info

Publication number
EP2514911B1
EP2514911B1 EP11003342.0A EP11003342A EP2514911B1 EP 2514911 B1 EP2514911 B1 EP 2514911B1 EP 11003342 A EP11003342 A EP 11003342A EP 2514911 B1 EP2514911 B1 EP 2514911B1
Authority
EP
European Patent Office
Prior art keywords
pump
hydraulic
hydraulic pump
control
power
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP11003342.0A
Other languages
German (de)
French (fr)
Other versions
EP2514911A1 (en
Inventor
Christoph Huss
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Klemm Bohrtechnik GmbH
Original Assignee
Klemm Bohrtechnik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Klemm Bohrtechnik GmbH filed Critical Klemm Bohrtechnik GmbH
Priority to ES11003342T priority Critical patent/ES2427345T3/en
Priority to PL11003342T priority patent/PL2514911T3/en
Priority to EP11003342.0A priority patent/EP2514911B1/en
Publication of EP2514911A1 publication Critical patent/EP2514911A1/en
Application granted granted Critical
Publication of EP2514911B1 publication Critical patent/EP2514911B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH DRILLING; MINING
    • E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B7/00—Special methods or apparatus for drilling
    • E21B7/002—Drilling with diversely driven shafts extending into the borehole
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH DRILLING; MINING
    • E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B6/00—Drives for drilling with combined rotary and percussive action
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH DRILLING; MINING
    • E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B7/00—Special methods or apparatus for drilling
    • E21B7/02—Drilling rigs characterized by means for land transport with their own drive, e.g. skid mounting or wheel mounting
    • E21B7/022—Control of the drilling operation; Hydraulic or pneumatic means for activation or operation

Definitions

  • the invention relates to a drilling rig for earth drilling according to the preamble of claim 1 and to a method for operating a drilling rig for earth drilling according to the preamble of claim 12.
  • the drill comprises at least a first hydraulic drive and at least one second hydraulic drive, at least one first hydraulic pump and at least one second hydraulic pump, which are line-connected to the energy transfer by means of hydraulic fluid to the first hydraulic drive or the second hydraulic drive, a first pump control and a second pump control for controlling the the pump power to be delivered to the first hydraulic pump or the second hydraulic pump, and a rotary motor having an output shaft to which a torque for delivering a predetermined engine power is applied, by which the first hydraulic pump and the second hydraulic pump are driven.
  • a first hydraulic drive and at least a second hydraulic drive are operated, the first hydraulic drive by means of a first hydraulic pump, which is line connected to the first hydraulic drive, supplied with hydraulic fluid and the second hydraulic drive means a second hydraulic pump which is line-connected to the second hydraulic drive, is supplied with hydraulic fluid, a pump power to be output from the first hydraulic pump is controlled by a first pump controller and a pump power to be output from the second hydraulic pump is controlled by a second pump controller, and the hydraulic pumps are driven by a common rotary motor are.
  • the drill may be, for example, a dual head drilling apparatus with an inner linkage and an outer linkage.
  • the hydraulic drives can be provided, for example, to drive a drilling tool or percussion or serve as a drive of a chassis of the drill.
  • the hydraulic pumps are driven according to the invention by a common rotary motor, which is operated for example at rated speed.
  • a common rotary motor which is operated for example at rated speed.
  • the power consumed by the hydraulic pumps as a whole must be limited.
  • a hydraulic drill drill with a drive motor behind which a hydraulic pump set is connected, which consists of a transfer case and at least two hydraulic pumps.
  • a first pump supplies a slewing gear and a second pump supplies a striking mechanism.
  • US 3,910,358 describes a drilling machine for drilling, which uses two or more hydraulic motors for turning and driving a drill, wherein the motors are supplied with hydraulic fluid from a single variable displacement pump which is remote from the drilling machine.
  • an object of the invention may be considered to provide a drilling rig and a method of operating the drilling rig, which are flexibly adaptable to different operating modes.
  • the drilling apparatus includes adjusting means for adjusting a distribution of the motor power of the rotary motor between the first hydraulic pump and the second hydraulic pump.
  • the first hydraulic pump can have a maximum power of 60% and the second hydraulic pump record a maximum power of 40% of the total motor power of the rotary motor.
  • This distribution ratio can be changed variably by means of the adjusting device by an operator of the drilling device, the sum of the maximum powers of the hydraulic pumps remaining constant and in particular being able to correspond to the maximum output power of the rotary motor.
  • the power of the hydraulic pumps can be externally adapted to changing operating conditions and, for example, the power of one of the pumps can be set to a predetermined value.
  • the pump controls of the hydraulic pumps are preferably designed for power control of the first hydraulic pump or the second hydraulic pump.
  • the first hydraulic pump preferably comprises a first power control device and the second hydraulic pump a second power control device, with which a predetermined power of the pump is adjustable or regulated.
  • the hydraulic pumps are therefore preferably controlled individually by their respective pump control.
  • the first pump control has a first adjustment device and the second pump control has a second adjustment device, that the first adjustment device is designed to set a delivery flow of the first hydraulic pump as a function of a working pressure in a pressure line of the first hydraulic pump and in that the second adjusting device is designed to set a delivery flow of the second hydraulic pump as a function of a working pressure in a pressure line of the second hydraulic pump.
  • the adjusting device may have an adjusting cylinder for adjusting the hydraulic pump.
  • the adjusting devices are preferably designed so that a power control along a hyperbolic power curve in a pressure-volume flow diagram, which is also referred to as a performance diagram of the pump takes place.
  • a power control along a hyperbolic power curve in a pressure-volume flow diagram which is also referred to as a performance diagram of the pump takes place.
  • the flow rate of the pump is adjusted depending on the prevailing in the pressure line of the pump working pressure or a pressure difference between the pressure and a suction line, that the product of flow and pressure and thus the performance of the pump remains constant.
  • the first adjusting device can be acted upon by a first actuating pressure corresponding to the working pressure of the first hydraulic pump and that the second adjusting device can be acted upon by a second actuating pressure corresponding to the working pressure of the second hydraulic pump.
  • actuating pressure which corresponds to the pressure in the pressure line, the flow rate can be adjusted or regulated as a function of the working pressure.
  • the distribution of the engine power between the hydraulic pumps is preferably provided by the fact that the first pump control has a first control device which can be acted upon by a first control signal of the adjusting device for limiting the power and / or increasing the power of the first hydraulic pump and the second pump control has a second control device, which can be acted upon to limit the power and / or increase the power of the second hydraulic pump with a second control signal of the adjusting device.
  • the setting device is thus preferably designed to provide a control signal at both pump controls, in particular simultaneously, with which the power of the respective pump can be individually increased or reduced.
  • the control signals preferably act such that the power of one of the hydraulic pumps is raised and the power of the other hydraulic pump, in particular by the same amount, is lowered.
  • control signals are electrical, hydraulic and / or pneumatic control signals.
  • control signal may be an electric signal acting on an electromagnet or a control pressure acting on a control piston.
  • the setting device is set up, as a first control signal, a first control pressure and as a second control signal, a second control pressure provide. It is basically possible that the control pressures have different sizes.
  • the setting device is preferably set up to set the second control signal as a function of the first control signal. Due to the dependent control signals, the power of the hydraulic pumps can be changed in a predetermined ratio to each other.
  • the setting device is set up to provide control signals of the same size but opposite direction of action to the first and the second pump control. This makes it possible in a simple manner, with the control signals to achieve a power increase of the first hydraulic pump and a power reduction equal amount of the second hydraulic pump or vice versa.
  • the setting device is set up to lower the second control signal when the first control signal is raised and to raise it when the first control signal is lowered.
  • a defined, equal pilot signal can be provided at both control devices, which corresponds, for example, to a power split of 50% to 50%.
  • This ratio can be changed to a predetermined end ratio of, for example, 100% to 0%.
  • the change of the control signals is therefore preferably in the opposite direction, wherein, more preferably, the amount of increase of the one signal is equal to the amount of decrease of the second signal.
  • the setting device is set up to provide identical control signals to the first pump control and the second pump control, wherein the control signal in the first hydraulic pump in the direction of a reduction of the pump power, in particular the flow rate, and in the second hydraulic pump in the direction of an increase the pump power, in particular the flow rate, acts or vice versa.
  • a control pressure acting on both control devices in one of the control devices can adjust the adjusting device in a first direction and in the other control device in an opposite direction.
  • a comfortable operation of the adjusting device can be achieved in that the adjusting device has an operating element with which a distribution ratio of the motor power of the rotary motor between the first hydraulic pump and the second hydraulic pump, in particular manually and / or automatically adjustable.
  • the power adjustment of the hydraulic pump can therefore be done with a single control element or controller.
  • the operating element makes it possible in a simple manner, for example, to increase the power of a hydraulic pump under changed operating conditions, while at the same time ensuring that the power of the other pump is lowered, so that overloading of the motor is avoided.
  • the operating element may be a user-operable by a user control element, such as a potentiometer act.
  • a user control element such as a potentiometer act.
  • an adjustment that automatically or automatically adjusts the performance of the pump in response to switched consumers of the pump.
  • a sensor arrangement may be provided which determines the number and / or the power of the consumers, in particular the hydraulic drives. These determined values can be provided via a data connection to the setting device. The distribution ratio between the hydraulic pumps can then be set independently or automatically depending on the measured values.
  • Fig. 1 shows a pump assembly having a first pump unit 10 and a second pump unit 110.
  • the first pump unit 10 includes a first hydraulic pump 12 and the second pump unit 110 includes a second hydraulic pump 112.
  • the hydraulic pumps 12, 112 are driven by a common rotary motor 2, which has a rotating output shaft 4.
  • the rotary motor 2 may be, for example, a diesel engine or an electric motor.
  • the hydraulic pumps 12, 112 are driven either directly or via a transfer case of the output shaft 4 of the rotary motor 2.
  • the hydraulic pumps 12, 112 have a first drive shaft 16 and a second drive shaft 116, which is coupled to the output shaft 4 of the rotary motor 2, or the pumps are mounted directly on a common shaft.
  • the hydraulic pump 12 of the first pump unit 10 is connected on the input side to a suction line 13 and on the output side to a pressure line 14.
  • the hydraulic pump 112 of the second pump unit 110 is connected on the input side to a suction line 113 and on the output side to a pressure line 114.
  • Hydraulic drives 11, 111 are line connected via the pressure lines 14, 114 with the hydraulic pump 12 and 112, respectively, and are driven by a hydraulic fluid delivered by the hydraulic pump 12.
  • a respective control valve 17 or 117 can be arranged between the hydraulic pumps 12, 112 and the hydraulic drives 11, 111.
  • the pump units 10, 110 are comparable in terms of their construction, so that initially a general description of a pump unit 10, 110 follows.
  • Embodiments of a pump unit 10, 110 are in the FIGS. 2 to 4 shown.
  • a hydraulic pump 12, 112 and at least one further, not shown hydraulic pump is driven.
  • the hydraulic pump 12, 112 delivers from a tank 39.
  • the pump unit 10, 110 comprises a pump control 18, 118, which may also be referred to as pump control, in particular power control, of the hydraulic pump 12, 112.
  • pump control in particular power control
  • the power consumed by the hydraulic pump 12, 112 can be adjusted or regulated to a predetermined maximum value.
  • the delivery rate of the hydraulic pump 12, 112 is set in dependence on a pressure prevailing in the pressure line 14, 114 pressure.
  • the control valve 30 is on the input side connected via a connection channel 37 to the pressure line 14, 114 and on the other hand via a tank channel 38 to the tank 39 line connected.
  • the actuating cylinder 20 comprises a cylinder housing 21, in which a control piston 24 is arranged longitudinally displaceable.
  • the adjusting piston 24 acts via a piston rod 29 fixed thereto on an adjusting element of the hydraulic pump 12, 112, with which the delivery volume of the hydraulic pump 12 can be adjusted.
  • the actuating piston 24 has a first piston surface 25 and a second piston surface 26, which are oriented opposite to each other.
  • the first piston surface 25 delimits a first pressure chamber 22 and the second piston surface 26 delimits a second pressure chamber 23 of the actuating cylinder 20.
  • the first pressure chamber 22 is connected via a first connecting channel 27 and the second pressure chamber 23 is conductively connected to the control valve 30 via a second connecting channel 28.
  • the hyperbolic behavior is achieved by a lever mechanism 50.
  • the lever mechanism 50 has a lever 52, which is rotatably mounted about a rotation axis 51 and comprises a first lever arm 53 and a second lever arm 54.
  • a hydraulic cylinder 40 On the piston rod 29 of the adjusting piston 24, a hydraulic cylinder 40 is mounted, which moves along with the adjusting piston 24 along a lever arm b and with the pressure prevailing in the pressure line 14, 114 pump pressure p P is acted upon.
  • the hydraulic cylinder 40 has a cylinder housing 41 with a control piston 42 guided longitudinally displaceably therein.
  • the actuating piston 42 acts on the first lever arm 53 via a piston rod 43.
  • a pressure chamber 44 delimited by a piston surface 46 of the actuating piston 42 is line-connected via a control channel 34 to the pressure line 14, 114 of the hydraulic pump 12, 112.
  • the actuating cylinder 20 moves in the direction of maximum delivery volume V s max .
  • the control valve 30 is displaced to the right against the compression spring 31 and moves the actuating cylinder 20 in the direction minimum delivery volume V S min .
  • the pump controller 18, 118 has a control device 60 for increasing the power or lowering the power of the hydraulic pump 12, 112.
  • the control device 60 is designed to adjust the power curve of the hydraulic pump 12, 112 via a control signal p s or to adapt it to different operating states. Thus, the performance hyperbola can be shifted to higher or lower powers.
  • Fig. 2 shows an embodiment of the pump control 18, 118 with an electrical control device 60, by means of which the power of the hydraulic pump 12, 112 can be adjusted via an electrical control signal p s .
  • the control device 60 can in particular have an electromagnet.
  • the Figures 3 and 4 show an embodiment of the pump control 18 with a hydraulic control device 60.
  • the setting of the power curve via a hydraulic or pneumatic control cylinder 62.
  • the control cylinder 62 includes a cylinder housing 64 in which a control piston 66 is mounted longitudinally displaceable.
  • the control pressure p s acts on a control surface 67 or 68 of the actuating piston 66th
  • the power hyperbola is shifted to the left in the power diagram, which corresponds to a lower power P.
  • the maximum pressure p max and the maximum delivery rate Q max preferably remain the same.
  • Fig. 4 shows a kinematic reversal, the force F S does not counteract, but acts in the direction of the spring force F F , this strengthens and thus shifts the power hyperbola in the performance diagram to higher powers.
  • the control pressure p s By applying or increasing the control pressure p s , the power of the hydraulic pump 12, 112 is thus increased.
  • the second pump unit 110 with the second hydraulic pump 112 may be constructed corresponding to or equal to the first pump unit 10 with the first hydraulic pump 12.
  • An adjusting device 6 for distributing the engine power to the hydraulic pumps 12, 112 is set up to simultaneously provide a first control signal to the first pump controller 18 and to provide a second control signal to the second pump controller 118.
  • the pump control 18 of the first hydraulic pump 12 is designed, for example, as in Fig. 3 and the second pump controller 118 of the second hydraulic pump 112 are configured as shown in FIG Fig. 4 shown.
  • the power of the first hydraulic pump 12 can be lowered by a control pressure p s acting on both pump controls 12, 112, and at the same time the power of the second hydraulic pump 112 can be increased by a corresponding amount, so that the overall power remains the same.
  • Different distributions of the engine power to the hydraulic pumps 12, 112 can thus be achieved by providing the adjusting device 6 with the same control signals, in particular control pressures p s , at both pump controls 18, 118.
  • FIG. 3 shows three different operating states of the hydraulic pumps 12, 112.
  • the left-hand power diagrams respectively show power curves of the first hydraulic pump 12 and the right-hand power diagrams respectively show power curves of the second hydraulic pump 112.
  • the lower two power curves show an initial state in which both hydraulic pumps 12, 112 have 50% Record the total power P M of the rotary motor 2.
  • the distribution of the total power to the two hydraulic pumps 12, 112 can be changed.
  • the upper two performance diagrams show a state in which the performance of the first hydraulic pump 12 is lowered by a defined amount and the power of the second hydraulic pump 112 is raised by a corresponding amount.
  • a reverse situation is shown in which the power of the first hydraulic pump 12 is increased by a defined amount and the power of the second hydraulic pump 112 is lowered by a corresponding amount.
  • an operating element 70 for example with a rotary lever or knob, is provided.
  • the operating element 70 is set up to simultaneously adjust the pump power of both hydraulic pumps 12, 112. It may be possible to adjust the power of each pump between 0% and 100% of the engine power of the rotary motor 2 and thus flexibly divide the available engine power to the hydraulic pumps 12, 112.
  • the operating element 70 may in particular be a potentiometer.

Description

Die Erfindung betrifft ein Bohrgerät zum Erdbohren gemäß dem Oberbegriff des Anspruchs 1 sowie ein Verfahren zum Betreiben eines Bohrgeräts zum Erdbohren gemäß dem Oberbegriff des Anspruchs 12.The invention relates to a drilling rig for earth drilling according to the preamble of claim 1 and to a method for operating a drilling rig for earth drilling according to the preamble of claim 12.

Das Bohrgerät umfasst mindestens einen ersten Hydraulikantrieb und mindestens einen zweiten Hydraulikantrieb, mindestens eine erste Hydraulikpumpe und mindestens eine zweite Hydraulikpumpe, welche zur Energieübertragung mittels Hydraulikfluid mit dem ersten Hydraulikantrieb beziehungsweise dem zweiten Hydraulikantrieb leitungsverbunden sind, eine erste Pumpensteuerung und eine zweite Pumpensteuerung zum Steuern der von der ersten Hydraulikpumpe beziehungsweise zweiten Hydraulikpumpe abzugebenden Pumpenleistung und einen Drehmotor mit einer Abtriebswelle, an welcher zur Abgabe einer vorgegebenen Motorleistung ein Drehmoment anliegt, durch welches die erste Hydraulikpumpe und die zweite Hydraulikpumpe angetrieben sind.The drill comprises at least a first hydraulic drive and at least one second hydraulic drive, at least one first hydraulic pump and at least one second hydraulic pump, which are line-connected to the energy transfer by means of hydraulic fluid to the first hydraulic drive or the second hydraulic drive, a first pump control and a second pump control for controlling the the pump power to be delivered to the first hydraulic pump or the second hydraulic pump, and a rotary motor having an output shaft to which a torque for delivering a predetermined engine power is applied, by which the first hydraulic pump and the second hydraulic pump are driven.

Bei dem Verfahren zum Betreiben eines Bohrgeräts zum Erdbohren ist vorgesehen, dass mindestens ein erster Hydraulikantrieb und mindestens ein zweiter Hydraulikantrieb betrieben werden, der erste Hydraulikantrieb mittels einer ersten Hydraulikpumpe, welche mit dem ersten Hydraulikantrieb leitungsverbunden ist, mit Hydraulikfluid versorgt wird und der zweite Hydraulikantrieb mittels einer zweiten Hydraulikpumpe, welche mit dem zweiten Hydraulikantrieb leitungsverbunden ist, mit Hydraulikfluid versorgt wird, eine von der ersten Hydraulikpumpe abzugebende Pumpenleistung mittels einer ersten Pumpensteuerung und eine von der zweiten Hydraulikpumpe abzugebende Pumpenleistung mittels einer zweiten Pumpensteuerung gesteuert wird und die Hydraulikpumpen durch einen gemeinsamen Drehmotor angetrieben sind.In the method for operating a drill for earth drilling is provided that at least a first hydraulic drive and at least a second hydraulic drive are operated, the first hydraulic drive by means of a first hydraulic pump, which is line connected to the first hydraulic drive, supplied with hydraulic fluid and the second hydraulic drive means a second hydraulic pump which is line-connected to the second hydraulic drive, is supplied with hydraulic fluid, a pump power to be output from the first hydraulic pump is controlled by a first pump controller and a pump power to be output from the second hydraulic pump is controlled by a second pump controller, and the hydraulic pumps are driven by a common rotary motor are.

Bei dem Bohrgerät kann es sich beispielsweise um ein Gerät zum Doppelkopfbohren mit einen Innengestänge und einen Außengestänge handeln. Die Hydraulikantriebe können beispielsweise dazu vorgesehen sein, ein Bohrwerkzeug oder ein Schlagwerk anzutreiben oder als Antrieb eines Fahrwerks des Bohrgeräts dienen.The drill may be, for example, a dual head drilling apparatus with an inner linkage and an outer linkage. The hydraulic drives can be provided, for example, to drive a drilling tool or percussion or serve as a drive of a chassis of the drill.

Die Hydraulikpumpen sind erfindungsgemäß von einem gemeinsamen Drehmotor angetrieben, welcher beispielsweise mit Nenndrehzahl betrieben wird. Um die von dem Drehmotor abzugebende Gesamtleistung an die beiden Hydraulikpumpen zu begrenzen und so den Drehmotor vor einer Überlastung zu schützen, muss die von den Hydraulikpumpen insgesamt aufgenommene Leistung begrenzt werden. Hierzu ist es bekannt, die von dem Drehmotor gemeinsam angetriebenen Hydraulikpumpen so zu steuern, dass jede Pumpe jeweils eine vorgegebene maximale Leistung aufnehmen kann, beispielsweise 50% der Leistung des Drehmotors bei Nenngeschwindigkeit.The hydraulic pumps are driven according to the invention by a common rotary motor, which is operated for example at rated speed. In order to limit the total power to be delivered by the rotary motor to the two hydraulic pumps and thus to protect the rotary motor against an overload, the power consumed by the hydraulic pumps as a whole must be limited. For this purpose, it is known to control the jointly driven by the rotary motor hydraulic pumps so that each pump can each receive a predetermined maximum power, for example, 50% of the power of the rotary motor at rated speed.

Aus der DE 21 18 650 , die als nächstliegender Stand der Technik gilt, ist eine hydraulische Lafetten-Bohrmaschine mit einem Antriebsmotor bekannt, hinter welchen ein hydraulischer Pumpensatz geschaltet ist, der aus einem Verteilergetriebe und mindestens zwei hydraulischen Pumpen besteht. Eine erste Pumpe versorgt ein Drehwerk und eine zweite Pumpe versorgt ein Schlagwerk.From the DE 21 18 650 As the closest prior art, a hydraulic drill drill with a drive motor is known, behind which a hydraulic pump set is connected, which consists of a transfer case and at least two hydraulic pumps. A first pump supplies a slewing gear and a second pump supplies a striking mechanism.

US 3,910,358 beschreibt eine Bohrmaschine zum Erdbohren, welche zwei oder mehr hydraulische Motoren zum Drehen und Vortreiben eines Bohrers verwendet, wobei die Motoren mit Hydraulikfluid von einer einzelnen Verstellpumpe, welche entfernt von der Bohrmaschine angeordnet ist, versorgt werden. US 3,910,358 describes a drilling machine for drilling, which uses two or more hydraulic motors for turning and driving a drill, wherein the motors are supplied with hydraulic fluid from a single variable displacement pump which is remote from the drilling machine.

Als eine Aufgabe der Erfindung kann angesehen werden, ein Bohrgerät und ein Verfahren zum Betreiben des Bohrgeräts anzugeben, welche flexibel an unterschiedliche Betriebsarten anpassbar sind.As an object of the invention may be considered to provide a drilling rig and a method of operating the drilling rig, which are flexibly adaptable to different operating modes.

Die Aufgabe wird erfindungsgemäß durch ein Bohrgerät mit den Merkmalen des Anspruchs 1 und durch ein Verfahren mit den Merkmalen des Anspruchs 12 gelöst. Bevorzugte Ausführungsformen sind in den abhängigen Ansprüchen angegeben.The object is achieved by a drill with the features of claim 1 and by a method having the features of claim 12. Preferred embodiments are given in the dependent claims.

Das Bohrgerät umfasst eine Einstelleinrichtung zum Einstellen einer Verteilung der Motorleistung des Drehmotors zwischen der ersten Hydraulikpumpe und der zweiten Hydraulikpumpe.The drilling apparatus includes adjusting means for adjusting a distribution of the motor power of the rotary motor between the first hydraulic pump and the second hydraulic pump.

Bei dem Verfahren ist vorgesehen, dass unterschiedliche Verteilungen der Motorleistung des Drehmotors zwischen der ersten Hydraulikpumpe und der zweiten Hydraulikpumpe eingestellt werden.In the method, it is provided that different distributions of the engine power of the rotary motor between the first hydraulic pump and the second hydraulic pump are adjusted.

Ein Grundgedanke der Erfindung kann darin gesehen werden, die Gesamtmotorleistung des Drehmotors flexibel zwischen den Hydraulikpumpen aufzuteilen. So kann beispielsweise die erste Hydraulikpumpe eine maximale Leistung von 60% und die zweite Hydraulikpumpe eine maximale Leistung von 40% der Gesamtmotorleistung des Drehmotors aufnehmen. Dieses Verteilungsverhältnis kann mittels der Einstelleinrichtung durch einen Bediener des Bohrgeräts variabel verändert werden, wobei die Summe der Maximalleistungen der Hydraulikpumpen konstant bleiben und insbesondere der maximal abzugebenden Motorleistung des Drehmotors entsprechen können. Hierdurch kann die Leistung der Hydraulikpumpen von extern an veränderte Betriebsbedingungen angepasst werden und beispielsweise die Leistung einer der Pumpen auf einen vorgegebenen Wert eingestellt werden.A basic idea of the invention can be seen in the flexible division of the total motor power of the rotary motor between the hydraulic pumps. For example, the first hydraulic pump can have a maximum power of 60% and the second hydraulic pump record a maximum power of 40% of the total motor power of the rotary motor. This distribution ratio can be changed variably by means of the adjusting device by an operator of the drilling device, the sum of the maximum powers of the hydraulic pumps remaining constant and in particular being able to correspond to the maximum output power of the rotary motor. As a result, the power of the hydraulic pumps can be externally adapted to changing operating conditions and, for example, the power of one of the pumps can be set to a predetermined value.

Die Pumpensteuerungen der Hydraulikpumpen sind vorzugsweise zur Leistungsregelung der ersten Hydraulikpumpe beziehungsweise der zweiten Hydraulikpumpe ausgebildet. Die erste Hydraulikpumpe umfasst demnach vorzugsweise eine erste Leistungsregelungseinrichtung und die zweite Hydraulikpumpe eine zweite Leistungsregelungseinrichtung, mit welcher eine vorgegebene Leistung der Pumpe einstellbar oder regelbar ist. Die Hydraulikpumpen sind also vorzugsweise individuell durch ihre jeweilige Pumpensteuerung ansteuerbar.The pump controls of the hydraulic pumps are preferably designed for power control of the first hydraulic pump or the second hydraulic pump. Accordingly, the first hydraulic pump preferably comprises a first power control device and the second hydraulic pump a second power control device, with which a predetermined power of the pump is adjustable or regulated. The hydraulic pumps are therefore preferably controlled individually by their respective pump control.

In einer bevorzugten Ausgestaltung der Erfindung ist vorgesehen, dass die erste Pumpensteuerung eine erste Verstelleinrichtung und die zweite Pumpensteuerung eine zweite Verstelleinrichtung aufweist, dass die erste Verstelleinrichtung ausgebildet ist, einen Förderstrom der ersten Hydraulikpumpe in Abhängigkeit von einem Arbeitsdruck in einer Druckleitung der ersten Hydraulikpumpe einzustellen und dass die zweite Verstelleinrichtung ausgebildet ist, einen Förderstrom der zweiten Hydraulikpumpe in Abhängigkeit von einem Arbeitsdruck in einer Druckleitung der zweiten Hydraulikpumpe einzustellen. Die Verstelleinrichtung kann einen Verstellzylinder zur Verstellung der Hydraulikpumpe aufweisen.In a preferred embodiment of the invention, it is provided that the first pump control has a first adjustment device and the second pump control has a second adjustment device, that the first adjustment device is designed to set a delivery flow of the first hydraulic pump as a function of a working pressure in a pressure line of the first hydraulic pump and in that the second adjusting device is designed to set a delivery flow of the second hydraulic pump as a function of a working pressure in a pressure line of the second hydraulic pump. The adjusting device may have an adjusting cylinder for adjusting the hydraulic pump.

Die Verstelleinrichtungen sind vorzugsweise so ausgeführt, dass eine Leistungsregelung entlang einer hyperbolischen Leistungskurve in einem Druck-Volumenstrom-Diagramm, welches auch als Leistungsdiagramm der Pumpe bezeichnet wird, erfolgt. Hierzu wird der Förderstrom der Pumpe in Abhängigkeit des in der Druckleitung der Pumpe herrschenden Arbeitsdruckes beziehungsweise einer Druckdifferenz zwischen der Druck- und einer Saugleitung so eingestellt, dass das Produkt aus Förderstrom und Druck und damit die Leistung der Pumpe konstant bleibt.The adjusting devices are preferably designed so that a power control along a hyperbolic power curve in a pressure-volume flow diagram, which is also referred to as a performance diagram of the pump takes place. For this purpose, the flow rate of the pump is adjusted depending on the prevailing in the pressure line of the pump working pressure or a pressure difference between the pressure and a suction line, that the product of flow and pressure and thus the performance of the pump remains constant.

Weiterhin ist es nach der Erfindung bevorzugt, dass die erste Verstelleinrichtung mit einem dem Arbeitsdruck der ersten Hydraulikpumpe entsprechenden ersten Stelldruck beaufschlagbar ist und dass die zweite Verstelleinrichtung mit einem dem Arbeitsdruck der zweiten Hydraulikpumpe entsprechenden zweiten Stelldruck beaufschlagbar ist. Durch den auf die Verstelleinrichtung, insbesondere den Stellzylinder, wirkenden Stelldruck, welcher dem Druck in der Druckleitung entspricht, kann der Förderstrom in Abhängigkeit des Arbeitsdruckes eingestellt beziehungsweise geregelt werden.Furthermore, it is preferred according to the invention that the first adjusting device can be acted upon by a first actuating pressure corresponding to the working pressure of the first hydraulic pump and that the second adjusting device can be acted upon by a second actuating pressure corresponding to the working pressure of the second hydraulic pump. By acting on the adjusting device, in particular the actuating cylinder, actuating pressure, which corresponds to the pressure in the pressure line, the flow rate can be adjusted or regulated as a function of the working pressure.

Die Verteilung der Motorleistung zwischen den Hydraulikpumpen wird vorzugsweise dadurch bereitgestellt, dass die erste Pumpensteuerung eine erste Steuereinrichtung aufweist, welche zur Leistungsbegrenzung und/oder zur Leistungserhöhung der ersten Hydraulikpumpe mit einem ersten Steuersignal der Einstelleinrichtung beaufschlagbar ist und dass die zweite Pumpensteuerung eine zweite Steuereinrichtung aufweist, welche zur Leistungsbegrenzung und/oder zur Leistungserhöhung der zweiten Hydraulikpumpe mit einem zweiten Steuersignal der Einstelleinrichtung beaufschlagbar ist.The distribution of the engine power between the hydraulic pumps is preferably provided by the fact that the first pump control has a first control device which can be acted upon by a first control signal of the adjusting device for limiting the power and / or increasing the power of the first hydraulic pump and the second pump control has a second control device, which can be acted upon to limit the power and / or increase the power of the second hydraulic pump with a second control signal of the adjusting device.

Die Einstelleinrichtung ist also vorzugsweise dazu ausgebildet, an beiden Pumpensteuerungen, insbesondere gleichzeitig, ein Steuersignal bereitzustellen, mit welchem die Leistung der jeweiligen Pumpe individuell erhöht oder verringert werden kann. Durch das gleichzeitige Bereitstellen von Steuersignalen an beiden Hydraulikpumpen wird eine gleichzeitige Leistungsänderung beider Hydraulikpumpen erreicht. Die Steuersignale wirken bevorzugt derart, dass die Leistung einer der Hydraulikpumpen angehoben und die Leistung der anderen Hydraulikpumpe, insbesondere um den gleichen Betrag, abgesenkt wird.The setting device is thus preferably designed to provide a control signal at both pump controls, in particular simultaneously, with which the power of the respective pump can be individually increased or reduced. By simultaneously providing control signals to both hydraulic pumps, a simultaneous change in power of both hydraulic pumps is achieved. The control signals preferably act such that the power of one of the hydraulic pumps is raised and the power of the other hydraulic pump, in particular by the same amount, is lowered.

Erfindungsgemäß ist es bevorzugt, dass die Steuersignale elektrische, hydraulische und/oder pneumatische Steuersignale sind. Beispielsweise kann das Steuersignal ein auf einen Elektromagneten wirkendes elektrisches Signal oder ein auf einen Steuerkolben wirkender Steuerdruck sein.According to the invention, it is preferred that the control signals are electrical, hydraulic and / or pneumatic control signals. For example, the control signal may be an electric signal acting on an electromagnet or a control pressure acting on a control piston.

Bei der Verwendung von hydraulischen und/oder pneumatischen Steuersignalen ist es bevorzugt, dass die Einstelleinrichtung eingerichtet ist, als erstes Steuersignal einen ersten Steuerdruck und als zweites Steuersignal einen zweiten Steuerdruck bereitzustellen. Dabei ist es grundsätzlich möglich, dass die Steuerdrücke unterschiedliche Größen aufweisen.When using hydraulic and / or pneumatic control signals, it is preferred that the setting device is set up, as a first control signal, a first control pressure and as a second control signal, a second control pressure provide. It is basically possible that the control pressures have different sizes.

Vorzugsweise ist die Einstelleinrichtung eingerichtet, das zweite Steuersignal in Abhängigkeit des ersten Steuersignals einzustellen. Durch die voneinander abhängenden Steuersignale können die Leistungen der Hydraulikpumpen in einem vorgegebenen Verhältnis zueinander verändert werden.The setting device is preferably set up to set the second control signal as a function of the first control signal. Due to the dependent control signals, the power of the hydraulic pumps can be changed in a predetermined ratio to each other.

Weiterhin ist es bevorzugt, dass die Einstelleinrichtung eingerichtet ist, an der ersten und der zweiten Pumpensteuerung Steuersignale mit gleicher Größe, aber entgegengesetzter Wirkungsrichtung, bereitzustellen. Dies ermöglicht es auf einfache Weise, mit den Steuersignalen eine Leistungserhöhung der ersten Hydraulikpumpe und eine Leistungsabsenkung gleichen Betrages der zweiten Hydraulikpumpe oder umgekehrt zu erzielen.Furthermore, it is preferred that the setting device is set up to provide control signals of the same size but opposite direction of action to the first and the second pump control. This makes it possible in a simple manner, with the control signals to achieve a power increase of the first hydraulic pump and a power reduction equal amount of the second hydraulic pump or vice versa.

In einer weiteren bevorzugten Ausgestaltung ist die Einstelleinrichtung eingerichtet, das zweite Steuersignal bei einer Anhebung des ersten Steuersignals abzusenken und bei einer Absenkung des ersten Steuersignals anzuheben. Beispielsweise kann ein definiertes, gleiches Vorsteuersignal an beiden Steuereinrichtungen bereitgestellt werden, welches zum Beispiel einer Leistungsaufteilung von 50 % zu 50% entspricht. Durch eine Anhebung des ersten Steuersignals und eine gleichzeitige Absenkung des zweiten Steuersignals kann dieses Verhältnis bis zu einem vorgegebenen Endverhältnis von beispielsweise 100 % zu 0 % verändert werden. Die Änderung der Steuersignale ist also vorzugsweise entgegengerichtet, wobei weiter vorzugsweise der Betrag der Anhebung des einen Signals gleich dem Betrag der Absenkung des zweiten Signals ist.In a further preferred refinement, the setting device is set up to lower the second control signal when the first control signal is raised and to raise it when the first control signal is lowered. For example, a defined, equal pilot signal can be provided at both control devices, which corresponds, for example, to a power split of 50% to 50%. By increasing the first control signal and simultaneously lowering the second control signal, this ratio can be changed to a predetermined end ratio of, for example, 100% to 0%. The change of the control signals is therefore preferably in the opposite direction, wherein, more preferably, the amount of increase of the one signal is equal to the amount of decrease of the second signal.

Weiterhin ist es bevorzugt, dass die Einstelleinrichtung eingerichtet ist, gleiche Steuersignale an der ersten Pumpensteuerung und der zweiten Pumpensteuerung bereitzustellen, wobei das Steuersignal bei der ersten Hydraulikpumpe in Richtung einer Verkleinerung der Pumpenleistung, insbesondere des Förderstroms, und bei der zweiten Hydraulikpumpe in Richtung einer Vergrößerung der Pumpenleistung, insbesondere des Förderstroms, wirkt oder umgekehrt. Hierzu kann beispielsweise ein an beiden Steuereinrichtungen wirkender Steuerdruck bei einer der Steuereinrichtungen die Verstelleinrichtung in eine erste Richtung und bei der anderen Steuereinrichtung in eine entgegengesetzte Richtung verstellen.Furthermore, it is preferred that the setting device is set up to provide identical control signals to the first pump control and the second pump control, wherein the control signal in the first hydraulic pump in the direction of a reduction of the pump power, in particular the flow rate, and in the second hydraulic pump in the direction of an increase the pump power, in particular the flow rate, acts or vice versa. For this purpose, for example, a control pressure acting on both control devices in one of the control devices can adjust the adjusting device in a first direction and in the other control device in an opposite direction.

Eine komfortable Bedienung der Einstelleinrichtung lässt sich dadurch erreichen, dass die Einstelleinrichtung ein Bedienelement aufweist, mit welchem ein Verteilungsverhältnis der Motorleistung des Drehmotors zwischen der ersten Hydraulikpumpe und der zweiten Hydraulikpumpe, insbesondere manuell und/oder automatisch, einstellbar ist. Die Leistungsverstellung der Hydraulikpumpen kann demnach mit einem einzigen Bedienelement oder Regler erfolgen. Das Bedienelement ermöglicht es auf einfache Weise, bei veränderten Betriebsbedingungen die Leistung einer Hydraulikpumpe beispielsweise zu erhöhen, wobei gleichzeitig sichergestellt wird, dass die Leistung der anderen Pumpe abgesenkt wird, so dass eine Überlastung des Motors vermieden wird.A comfortable operation of the adjusting device can be achieved in that the adjusting device has an operating element with which a distribution ratio of the motor power of the rotary motor between the first hydraulic pump and the second hydraulic pump, in particular manually and / or automatically adjustable. The power adjustment of the hydraulic pump can therefore be done with a single control element or controller. The operating element makes it possible in a simple manner, for example, to increase the power of a hydraulic pump under changed operating conditions, while at the same time ensuring that the power of the other pump is lowered, so that overloading of the motor is avoided.

Bei dem Bedienelement kann es sich um ein durch einen Anwender manuell betätigbares Bedienelement, beispielsweise ein Potentiometer, handeln. Weiterhin ist es auch möglich, eine Einstelleinrichtung zu verwenden, welche die Leistungen der Pumpen in Abhängigkeit von eingeschalteten Verbrauchern der Pumpen selbstständig oder automatisch einstellt. Hierzu kann beispielsweise eine Sensoranordnung vorgesehen sein, welche die Anzahl und/oder die Leistung der Verbraucher, insbesondere der Hydraulikantriebe, ermittelt. Diese ermittelten Werte können über eine Datenverbindung an der Einstelleinrichtung bereitgestellt werden. Das Verteilungsverhältnis zwischen den Hydraulikpumpen kann dann selbstständig oder automatisch in Abhängigkeit der gemessenen Werte eingestellt werden.The operating element may be a user-operable by a user control element, such as a potentiometer act. Furthermore, it is also possible to use an adjustment that automatically or automatically adjusts the performance of the pump in response to switched consumers of the pump. For this purpose, for example, a sensor arrangement may be provided which determines the number and / or the power of the consumers, in particular the hydraulic drives. These determined values can be provided via a data connection to the setting device. The distribution ratio between the hydraulic pumps can then be set independently or automatically depending on the measured values.

Die Erfindung wird nachfolgend anhand der beigefügten, schematischen Zeichnungen weiter erläutert. Hierin zeigt:

Fig. 1:
eine erfindungsgemäße Pumpenanordnung eines Bohrgeräts;
Fig. 2:
eine elektrische Leistungsregelung einer Hydraulikpumpe;
Fig. 3:
eine erste hydraulische oder pneumatische Leistungsregelung einer Hydraulikpumpe;
Fig. 4:
eine zweite hydraulische oder pneumatische Leistungsregelung einer Hydraulikpumpe; und
Fig. 5:
Leistungsdiagramme von Hydraulikpumpen bei unterschiedlichen Betriebszuständen sowie ein Bedienelement zur Leistungsregelung.
The invention is explained below with reference to the accompanying schematic drawings. Hereby shows:
Fig. 1:
a pump assembly according to the invention a drill;
Fig. 2:
an electric power control of a hydraulic pump;
3:
a first hydraulic or pneumatic power control of a hydraulic pump;
4:
a second hydraulic or pneumatic power control of a hydraulic pump; and
Fig. 5:
Performance diagrams of hydraulic pumps in different operating states as well as a control element for power control.

Einander entsprechende Komponenten sind in allen Figuren mit denselben Bezugszeichen gekennzeichnet.Corresponding components are identified in all figures with the same reference numerals.

Fig. 1 zeigt eine Pumpenanordnung mit einer ersten Pumpeneinheit 10 und einer zweiten Pumpeneinheit 110. Die erste Pumpeneinheit 10 umfasst eine erste Hydraulikpumpe 12 und die zweite Pumpeneinheit 110 umfasst eine zweite Hydraulikpumpe 112. Fig. 1 shows a pump assembly having a first pump unit 10 and a second pump unit 110. The first pump unit 10 includes a first hydraulic pump 12 and the second pump unit 110 includes a second hydraulic pump 112.

Die Hydraulikpumpen 12, 112 sind durch einen gemeinsamen Drehmotor 2, welcher eine rotierende Abtriebswelle 4 aufweist, angetriebenen. Bei dem Drehmotor 2 kann es sich beispielsweise um einen Dieselmotor oder einen Elektromotor handeln.The hydraulic pumps 12, 112 are driven by a common rotary motor 2, which has a rotating output shaft 4. The rotary motor 2 may be, for example, a diesel engine or an electric motor.

Die Hydraulikpumpen 12, 112 sind entweder direkt oder über ein Verteilergetriebe von der Abtriebswelle 4 des Drehmotors 2 angetrieben. Die Hydraulikpumpen 12, 112 weisen eine ersten Antriebswelle 16 beziehungsweise eine zweite Antriebswelle 116 auf, die mit der Abtriebswelle 4 des Drehmotors 2 gekoppelt ist, oder die Pumpen sind direkt auf einer gemeinsamen Welle montiert.The hydraulic pumps 12, 112 are driven either directly or via a transfer case of the output shaft 4 of the rotary motor 2. The hydraulic pumps 12, 112 have a first drive shaft 16 and a second drive shaft 116, which is coupled to the output shaft 4 of the rotary motor 2, or the pumps are mounted directly on a common shaft.

Die Hydraulikpumpe 12 der ersten Pumpeneinheit 10 ist eingangsseitig an eine Saugleitung 13 und ausgangsseitig an eine Druckleitung 14 angeschlossen. Die Hydraulikpumpe 112 der zweiten Pumpeneinheit 110 ist eingangsseitig an eine Saugleitung 113 und ausgangsseitig an eine Druckleitung 114 angeschlossen. Hydraulikantriebe 11, 111 sind über die Druckleitungen 14, 114 mit der Hydraulikpumpe 12 beziehungsweise 112 leitungsverbunden und werden über ein von der Hydraulikpumpe 12 gefördertes Hydraulikfluid angetrieben. Zwischen den Hydraulikpumpen 12, 112 und den Hydraulikantrieben 11, 111 kann, wie dargestellt, jeweils ein Stellventil 17 beziehungsweise 117 angeordnet sein.The hydraulic pump 12 of the first pump unit 10 is connected on the input side to a suction line 13 and on the output side to a pressure line 14. The hydraulic pump 112 of the second pump unit 110 is connected on the input side to a suction line 113 and on the output side to a pressure line 114. Hydraulic drives 11, 111 are line connected via the pressure lines 14, 114 with the hydraulic pump 12 and 112, respectively, and are driven by a hydraulic fluid delivered by the hydraulic pump 12. As shown, a respective control valve 17 or 117 can be arranged between the hydraulic pumps 12, 112 and the hydraulic drives 11, 111.

Die Pumpeneinheiten 10, 110 sind hinsichtlich ihres Aufbaus vergleichbar, so dass nachstehend zunächst allgemein eine Beschreibung einer Pumpeneinheit 10, 110 erfolgt.The pump units 10, 110 are comparable in terms of their construction, so that initially a general description of a pump unit 10, 110 follows.

Ausführungsbeispiele einer Pumpeneinheit 10, 110 sind in den Figuren 2 bis 4 dargestellt. Durch den Drehmotor 2 wird eine Hydraulikpumpe 12, 112 und mindestens eine weitere, nicht dargestellte Hydraulikpumpe angetrieben. Die Hydraulikpumpe 12, 112 fördert aus einem Tank 39.Embodiments of a pump unit 10, 110 are in the FIGS. 2 to 4 shown. By the rotary motor 2, a hydraulic pump 12, 112 and at least one further, not shown hydraulic pump is driven. The hydraulic pump 12, 112 delivers from a tank 39.

Die Pumpeneinheit 10, 110 umfasst eine Pumpensteuerung 18, 118, welche auch als Pumpenregelung, insbesondere Leistungsregelung, der Hydraulikpumpe 12, 112 bezeichnet werden kann. Mit der Pumpensteuerung 18, 118 kann die von der Hydraulikpumpe 12, 112 aufgenommene Leistung auf einen vorgegebenen, maximalen Wert eingestellt beziehungsweise geregelt werden. Hierzu wird in Abhängigkeit von einem in der Druckleitung 14, 114 herrschenden Druck die Fördermenge der Hydraulikpumpe 12, 112 eingestellt.The pump unit 10, 110 comprises a pump control 18, 118, which may also be referred to as pump control, in particular power control, of the hydraulic pump 12, 112. With the pump control 18, 118, the power consumed by the hydraulic pump 12, 112 can be adjusted or regulated to a predetermined maximum value. For this purpose, the delivery rate of the hydraulic pump 12, 112 is set in dependence on a pressure prevailing in the pressure line 14, 114 pressure.

Die Verstellung der Fördermenge der Hydraulikpumpe 12, 112, welche insbesondere eine Axialkolbenpumpe sein kann, erfolgt über eine Verstelleinrichtung 19 in Form eines Stellzylinders 20, welcher von einem Stellventil 30 in Richtung eines minimalen Fördervolumens (VS min) oder maximalen Fördervolumens (VS max) pro Umdrehung bewegt werden kann. Das Stellventil 30 ist eingangsseitig einerseits über einen Anschlusskanal 37 mit der Druckleitung 14, 114 und andererseits über einen Tankkanal 38 mit dem Tank 39 leitungsverbunden.The adjustment of the delivery rate of the hydraulic pump 12, 112, which may be in particular an axial piston pump, via an adjusting device 19 in the form of a control cylinder 20, which by a control valve 30 in the direction of a minimum delivery volume (V S min ) or maximum delivery volume (V S max ) can be moved per revolution. The control valve 30 is on the input side connected via a connection channel 37 to the pressure line 14, 114 and on the other hand via a tank channel 38 to the tank 39 line connected.

Der Stellzylinder 20 umfasst ein Zylindergehäuse 21, in welchem längsverschieblich ein Stellkolben 24 angeordnet ist. Der Stellkolben 24 wirkt über eine daran befestigte Kolbenstange 29 auf ein Stellelement der Hydraulikpumpe 12, 112, mit welchem das Fördervolumen der Hydraulikpumpe 12 eingestellt werden kann.The actuating cylinder 20 comprises a cylinder housing 21, in which a control piston 24 is arranged longitudinally displaceable. The adjusting piston 24 acts via a piston rod 29 fixed thereto on an adjusting element of the hydraulic pump 12, 112, with which the delivery volume of the hydraulic pump 12 can be adjusted.

Der Stellkolben 24 weist eine erste Kolbenfläche 25 und eine zweite Kolbenfläche 26 auf, die entgegengesetzt zueinander orientiert sind. Die erste Kolbenfläche 25 begrenzt eine erste Druckkammer 22 und die zweite Kolbenfläche 26 begrenzt eine zweite Druckkammer 23 des Stellzylinders 20. Die erste Druckkammer 22 ist über einen ersten Verbindungskanal 27 und die zweite Druckkammer 23 ist über einen zweiten Verbindungskanal 28 mit dem Stellventil 30 leitungsverbunden.The actuating piston 24 has a first piston surface 25 and a second piston surface 26, which are oriented opposite to each other. The first piston surface 25 delimits a first pressure chamber 22 and the second piston surface 26 delimits a second pressure chamber 23 of the actuating cylinder 20. The first pressure chamber 22 is connected via a first connecting channel 27 and the second pressure chamber 23 is conductively connected to the control valve 30 via a second connecting channel 28.

Die hydraulische Leistung (P) der Hydraulikpumpe 12 ergibt sich durch den in der Druckleitung 14, 114 herrschenden Pumpendruck (p) beziehungsweise eine Druckdifferenz zwischen der Druckleitung 14, 114 und der Saugleitung 13, 113 multipliziert mit dem Volumenstrom (Q) der Pumpe. Wenn eine Pumpe eine konstante Leistung abgreifen soll, ergibt sich aus der Bedingung P = p * Q = const. ein hyperbolischer Kurvenverlauf in einem Leistungsdiagramm der Pumpe, wie in Fig. 5 dargestellt. Diese sogenannte Leistungshyperbel ist auf der Ordinate durch den maximal zulässigen Druck pmax. und auf der Abszisse durch den maximalen Volumenstrom Qmax., welcher sich aus der Nenndrehzahl des Antriebsmotors beziehungsweise Drehmotors 2 multipliziert mit dem maximalen Fördervolumen pro Umdrehung ergibt, begrenzt.The hydraulic power (P) of the hydraulic pump 12 results from the pressure in the pressure line 14, 114 prevailing pump pressure (p) or a pressure difference between the pressure line 14, 114 and the suction line 13, 113 multiplied by the volume flow (Q) of the pump. If a pump is to achieve a constant power, the condition P = p * Q = const results. a hyperbolic curve in a performance diagram of the pump, as in Fig. 5 shown. This so-called power hyperbola is on the ordinate by the maximum allowable pressure p max. and on the abscissa by the maximum volume flow Q max. , which one itself from the rated speed of the drive motor or rotary motor 2 multiplied by the maximum delivery volume per revolution, limited.

Das hyperbolische Verhalten wird durch einen Hebelmechanismus 50 erreicht. Der Hebelmechanismus 50 weist einen Hebel 52 auf, welcher um eine Drehachse 51 drehbar gelagert ist und einen ersten Hebelarm 53 und einen zweiten Hebelarm 54 umfasst.The hyperbolic behavior is achieved by a lever mechanism 50. The lever mechanism 50 has a lever 52, which is rotatably mounted about a rotation axis 51 and comprises a first lever arm 53 and a second lever arm 54.

Auf den Hebel 52 wirken linksdrehende und rechtsdrehende Momente. Bei der in den Figuren 2 bis 4 dargestellten Anordnung ergeben sich die linksdrehenden Momente aus einer Federkraft FF des Stellventils 30 multipliziert mit einem Hebelarm a, welcher einen Abstand zwischen dem Angriffspunkt der Federkraft FF auf den zweiten Hebelarm 54 und der Drehachse 51 darstellt. Das Stellventil 30 ist hierzu mit einer Druckfeder 31 beaufschlagt, welche das Ventil 30 in der dargestellten Ausführungsform nach links verschiebt.On the lever 52 act left-handed and right-handed moments. In the in the FIGS. 2 to 4 The arrangement shown, the left-handed moments of a spring force F F of the control valve 30 multiplied by a lever arm a, which represents a distance between the point of application of the spring force F F on the second lever arm 54 and the rotation axis 51. The control valve 30 is for this purpose acted upon by a compression spring 31, which shifts the valve 30 in the illustrated embodiment to the left.

Auf der Kolbenstange 29 des Stellkolbens 24 ist ein Hydraulikzylinder 40 montiert, welcher sich zusammen mit dem Stellkolben 24 entlang eines Hebelarmes b bewegt und mit dem in der Druckleitung 14, 114 herrschenden Pumpendruck pP beaufschlagt wird. Der Hydraulikzylinder 40 weist hierzu ein Zylindergehäuse 41 mit einem darin längverschieblich geführten Stellkolben 42 auf. Der Stellkolben 42 wirkt über eine Kolbenstange 43 auf den ersten Hebelarm 53. Eine von einer Kolbenfläche 46 des Stellkolbens 42 begrenzte Druckkammer 44 ist über einen Steuerkanal 34 mit der Druckleitung 14, 114 der Hydraulikpumpe 12, 112 leitungsverbunden.On the piston rod 29 of the adjusting piston 24, a hydraulic cylinder 40 is mounted, which moves along with the adjusting piston 24 along a lever arm b and with the pressure prevailing in the pressure line 14, 114 pump pressure p P is acted upon. For this purpose, the hydraulic cylinder 40 has a cylinder housing 41 with a control piston 42 guided longitudinally displaceably therein. The actuating piston 42 acts on the first lever arm 53 via a piston rod 43. A pressure chamber 44 delimited by a piston surface 46 of the actuating piston 42 is line-connected via a control channel 34 to the pressure line 14, 114 of the hydraulic pump 12, 112.

Der Hebelarm b ergibt sich aus einem Abstand zwischen dem Angriffspunkt des Hydraulikzylinders 40 auf den ersten Hebelarm 53 und der Drehachse 51 des Hebelmechanismus 50. Aus dem Pumpendruck pP multipliziert mit der Kolbenfläche 46 des Hydraulikzylinders 40 ergibt sich eine Kraft Fp. Diese Kraft multipliziert mit dem Hebelarm b - dieser ist bei konstanter Drehzahl proportional zum Volumenstrom Q - ergibt die rechtsdrehenden Momente des Hebelmechanismus 50. Hieraus folgt eine Gleichgewichtsbedingung: FF*a = Fp*b.The lever arm b results from a distance between the point of application of the hydraulic cylinder 40 on the first lever arm 53 and the axis of rotation 51 of the lever mechanism 50. From the pump pressure p P multiplied by the piston surface 46 of the hydraulic cylinder 40 results in a force Fp. This force multiplied by the lever arm b - this is proportional to the volume flow Q at constant speed - gives the dextrorotatory moments of the lever mechanism 50. From this follows an equilibrium condition: F F * a = F p * b.

Solange FF*a größer Fp*b ist, bewegt sich der Stellzylinder 20 in Richtung maximales Fördervolumen Vs max. Sobald FF*a kleiner Fp*b ist, wird das Stellventil 30 gegen die Druckfeder 31 nach rechts verschoben und bewegt den Stellzylinder 20 in Richtung minimales Fördervolumen VS min. Das Stellventil 30 ist als Proportionalventil ausgeführt, so dass es sich bei FF*a = Fp*b in einer Regelstellung befindet. Bei kleinem Hebelarm b, was einer geringen Fördermenge entspricht, ist eine hohe Kraft Fp und somit ein hoher Pumpendruck pP erforderlich, um die Pumpe zurückzuschwenken. Mit steigender Fördermenge vergrößert sich der Hebelarm b und die Abregelung erfolgt bereits bei geringerem Pumpendruck pP, wodurch die hyperbolische Form der Leistungskurve generiert wird.As long as F F * a is greater than F p * b, the actuating cylinder 20 moves in the direction of maximum delivery volume V s max . As soon as F F * a is smaller F p * b, the control valve 30 is displaced to the right against the compression spring 31 and moves the actuating cylinder 20 in the direction minimum delivery volume V S min . The control valve 30 is designed as a proportional valve, so that it is in a control position at F F * a = F p * b. With a small lever arm b, which corresponds to a low delivery rate, a high force Fp and thus a high pump pressure p P is required to return the pump. With increasing flow rate, the lever arm b increases and the reduction takes place already at a lower pump pressure p P , whereby the hyperbolic shape of the power curve is generated.

Die Pumpensteuerung 18, 118 weist eine Steuereinrichtung 60 zur Leistungserhöhung oder Leistungsabsenkung der Hydraulikpumpe 12, 112 auf. Die Steuereinrichtung 60 ist ausgebildet, die Leistungskurve der Hydraulikpumpe 12, 112 über ein Steuersignal ps zu verstellen beziehungsweise an unterschiedliche Betriebszustände anzupassen. Es kann also die Leistungshyperbel hin zu höheren oder niedrigeren Leistungen verschoben werden.The pump controller 18, 118 has a control device 60 for increasing the power or lowering the power of the hydraulic pump 12, 112. The control device 60 is designed to adjust the power curve of the hydraulic pump 12, 112 via a control signal p s or to adapt it to different operating states. Thus, the performance hyperbola can be shifted to higher or lower powers.

Fig. 2 zeigt eine Ausführungsform der Pumpensteuerung 18, 118 mit einer elektrischen Steuereinrichtung 60, mittels welcher die Leistung der Hydraulikpumpe 12, 112 über ein elektrisches Steuersignal ps eingestellt werden kann. Die Steuereinrichtung 60 kann hierzu insbesondere einen Elektromagnet aufweisen. Fig. 2 shows an embodiment of the pump control 18, 118 with an electrical control device 60, by means of which the power of the hydraulic pump 12, 112 can be adjusted via an electrical control signal p s . For this purpose, the control device 60 can in particular have an electromagnet.

Die Figuren 3 und 4 zeigen eine Ausführungsform der Pumpensteuerung 18 mit einer hydraulischen Steuereinrichtung 60. Hierbei erfolgt die Einstellung der Leistungskurve über einen hydraulischen oder pneumatischen Steuerzylinder 62. Der Steuerzylinder 62 umfasst ein Zylindergehäuse 64, in welchem ein Stellkolben 66 längsverschieblich gelagert ist. Der Steuerdruck ps wirkt dabei auf eine Steuerfläche 67 beziehungsweise 68 des Stellkolbens 66.The Figures 3 and 4 show an embodiment of the pump control 18 with a hydraulic control device 60. In this case, the setting of the power curve via a hydraulic or pneumatic control cylinder 62. The control cylinder 62 includes a cylinder housing 64 in which a control piston 66 is mounted longitudinally displaceable. The control pressure p s acts on a control surface 67 or 68 of the actuating piston 66th

Bei der Ausführungsform gemäß Fig. 3 erzeugt die Steuereinrichtung 60 eine zusätzliche Kraft FS, welche der Federkraft FF entgegenwirkt und die Gleichgewichtsbedingung zu FF*a = Fp*b + FS*a beziehungsweise (FF - FS)*a = Fp*b verändert. Hierdurch wird die Leistungshyperbel im Leistungsdiagramm nach links verschoben, was einer geringeren Leistung P entspricht. Der maximale Druck pmax und die maximale Fördermenge Qmax bleiben hierbei vorzugsweise gleich. Durch ein Anlegen oder Erhöhen des Steuerdrucks ps wird somit die Leistung der Hydraulikpumpe 12, 112 reduziert.In the embodiment according to Fig. 3 The control device 60 generates an additional force F S , which counteracts the spring force F F and changes the equilibrium condition to F F * a = F p * b + F S * a or (F F - F S ) * a = F p * b , As a result, the power hyperbola is shifted to the left in the power diagram, which corresponds to a lower power P. The maximum pressure p max and the maximum delivery rate Q max preferably remain the same. By applying or increasing the control pressure p s , the power of the hydraulic pump 12, 112 is thus reduced.

Fig. 4 zeigt eine kinematische Umkehr, wobei die Kraft FS nicht entgegen, sondern in Richtung der Federkraft FF wirkt, diese verstärkt und somit die Leistungshyperbel im Leistungsdiagramm zu höheren Leistungen verschiebt. Durch ein Anlegen oder Erhöhen des Steuerdrucks ps wird somit die Leistung der Hydraulikpumpe 12, 112 erhöht. Fig. 4 shows a kinematic reversal, the force F S does not counteract, but acts in the direction of the spring force F F , this strengthens and thus shifts the power hyperbola in the performance diagram to higher powers. By applying or increasing the control pressure p s , the power of the hydraulic pump 12, 112 is thus increased.

Die zweite Pumpeneinheit 110 mit der zweiten Hydraulikpumpe 112 kann entsprechend oder gleich der ersten Pumpeneinheit 10 mit der ersten Hydraulikpumpe 12 aufgebaut sein.The second pump unit 110 with the second hydraulic pump 112 may be constructed corresponding to or equal to the first pump unit 10 with the first hydraulic pump 12.

Eine Einstelleinrichtung 6 zum Verteilen der Motorleistung auf die Hydraulikpumpen 12, 112 ist eingerichtet, gleichzeitig an der ersten Pumpensteuerung 18 ein erstes Steuersignal und an der zweiten Pumpensteuerung 118 ein zweites Steuersignal bereitzustellen.An adjusting device 6 for distributing the engine power to the hydraulic pumps 12, 112 is set up to simultaneously provide a first control signal to the first pump controller 18 and to provide a second control signal to the second pump controller 118.

In einer bevorzugten Ausführungsform der Erfindung ist die Pumpensteuerung 18 der ersten Hydraulikpumpe 12 beispielsweise so ausgeführt, wie in Fig. 3 gezeigt, und die zweite Pumpensteuerung 118 der zweiten Hydraulikpumpe 112 so ausgeführt, wie in der Fig. 4 dargestellt. Hierdurch lässt sich durch einen auf beide Pumpensteuerungen 12, 112 wirkenden, insbesondere gleichen, Steuerdruck ps die Leistung der ersten Hydraulikpumpe 12 absenken und gleichzeitig die Leistung der zweiten Hydraulikpumpe 112 um einen entsprechenden Betrag anheben, so dass die Gesamtleistung gleichbleibt. Unterschiedliche Verteilungen der Motorleistung auf die Hydraulikpumpen 12, 112 können somit dadurch erreicht werden, dass die Einstelleinrichtung 6 gleiche Steuersignale, insbesondere Steuerdrücke ps, an beiden Pumpensteuerungen 18, 118 bereitstellt.In a preferred embodiment of the invention, the pump control 18 of the first hydraulic pump 12 is designed, for example, as in Fig. 3 and the second pump controller 118 of the second hydraulic pump 112 are configured as shown in FIG Fig. 4 shown. As a result, the power of the first hydraulic pump 12 can be lowered by a control pressure p s acting on both pump controls 12, 112, and at the same time the power of the second hydraulic pump 112 can be increased by a corresponding amount, so that the overall power remains the same. Different distributions of the engine power to the hydraulic pumps 12, 112 can thus be achieved by providing the adjusting device 6 with the same control signals, in particular control pressures p s , at both pump controls 18, 118.

Fig. 5 zeigt drei verschiedene Betriebszustände der Hydraulikpumpen 12, 112. Die linken Leistungsdiagramme zeigen jeweils Leistungskurven der ersten Hydraulikpumpe 12 und die rechten Leistungsdiagramme zeigen jeweils Leistungskurven der zweiten Hydraulikpumpe 112. Die unteren beiden Leistungskurven zeigen dabei einen Ausgangszustand, bei welchem beide Hydraulikpumpen 12, 112 50 % der Gesamtleistung PM des Drehmotors 2 aufnehmen. Fig. 5 FIG. 3 shows three different operating states of the hydraulic pumps 12, 112. The left-hand power diagrams respectively show power curves of the first hydraulic pump 12 and the right-hand power diagrams respectively show power curves of the second hydraulic pump 112. The lower two power curves show an initial state in which both hydraulic pumps 12, 112 have 50% Record the total power P M of the rotary motor 2.

Durch die Einstelleinrichtung 6 kann die Verteilung der Gesamtleistung auf die beiden Hydraulikpumpen 12, 112 verändert werden. Die oberen beiden Leistungsdiagramme zeigen beispielsweise einen Zustand, in welchem die Leistung der ersten Hydraulikpumpe 12 um einen definierten Betrag abgesenkt und die Leistung der zweiten Hydraulikpumpe 112 um einen entsprechenden Betrag angehoben ist. Im mittleren Bereich der Figur ist ein umgekehrte Situation gezeigt, bei welcher die Leistung der ersten Hydraulikpumpe 12 um einen definierten Betrag angehoben und die Leistung der zweiten Hydraulikpumpe 112 um einen entsprechenden Betrag abgesenkt ist.By adjusting 6, the distribution of the total power to the two hydraulic pumps 12, 112 can be changed. For example, the upper two performance diagrams show a state in which the performance of the first hydraulic pump 12 is lowered by a defined amount and the power of the second hydraulic pump 112 is raised by a corresponding amount. In the middle portion of the figure, a reverse situation is shown in which the power of the first hydraulic pump 12 is increased by a defined amount and the power of the second hydraulic pump 112 is lowered by a corresponding amount.

Zur Verteilung der Leistung des Drehmotors 2 auf die Hydraulikpumpen 12, 112 ist eine Bedienelement 70, beispielsweise mit einem Drehhebel oder Drehknopf, vorgesehen. Das Bedienelement 70 ist eingerichtet, die Pumpenleistung beider Hydraulikpumpen 12, 112 gleichzeitig anzupassen. Dabei kann es möglich sein, die Leistung jeder Pumpe zwischen 0 % und 100 % der Motorleistung des Drehmotors 2 einzustellen und so die verfügbare Motorleistung flexibel auf die Hydraulikpumpen 12, 112 aufzuteilen. Bei dem Bedienelement 70 kann es sich insbesondere um ein Potentiometer handeln.For distributing the power of the rotary motor 2 to the hydraulic pumps 12, 112, an operating element 70, for example with a rotary lever or knob, is provided. The operating element 70 is set up to simultaneously adjust the pump power of both hydraulic pumps 12, 112. It may be possible to adjust the power of each pump between 0% and 100% of the engine power of the rotary motor 2 and thus flexibly divide the available engine power to the hydraulic pumps 12, 112. The operating element 70 may in particular be a potentiometer.

Claims (12)

  1. Drilling device for soil drilling with
    - at least a first hydraulic drive (11) and at least a second hydraulic drive (111),
    - at least a first hydraulic pump (12) and at least a second hydraulic pump (112), which, for the transmission of energy by means of hydraulic fluid, are line-connected to the first hydraulic drive (11) and the second hydraulic drive (111) respectively, and
    - a rotation motor (2) with an output shaft (4), to which, for the supply of a predetermined motor power, a torque is applied, through which the first hydraulic pump (12) and the second hydraulic pump (112) are driven, wherein the motor power of the rotation motor (2) is distributed between the first hydraulic pump (12) and the second hydraulic pump (112),
    characterized in that
    - a first pump control (18) and a second pump control (118) are provided for controlling the pump power to be supplied by the first hydraulic pump (12) and the second hydraulic pump (112) respectively,
    - in that a setting means (6) is provided for setting different distributions of the motor power of the rotation motor (2) between the first hydraulic pump (12) and the second hydraulic pump (112), and
    - in that the setting means (6) has an operating element (70), with which a distribution ratio of the motor power of the rotation motor (2) between the first hydraulic pump (12) and the second hydraulic pump (112) can be set.
  2. Drilling device according to claim 1,
    characterized in that
    the pump controls (18, 118) of the hydraulic pumps (12, 112) are designed for regulating the power of the first hydraulic pump (12) and the second hydraulic pump (112) respectively.
  3. Drilling device according to claim 1 or 2,
    characterized in that
    - the first pump control (18) has a first adjusting means (19) and the second pump control (118) has a second adjusting means (119),
    - in that the first adjusting means (19) is designed to set a delivery flow of the first hydraulic pump (12) as a function of an operating pressure in a pressure line (14) of the first hydraulic pump (12) and
    - in that the second adjusting means (119) is designed to set a delivery flow of the second hydraulic pump (112) as a function of an operating pressure in a pressure line (114) of the second hydraulic pump (112).
  4. Drilling device according to claim 3,
    characterized in that
    - a first actuating pressure corresponding to the operating pressure of the first hydraulic pump (12) can be applied to the first adjusting means (19)
    and
    - in that a second actuating pressure corresponding to the operating pressure of the second hydraulic pump (112) can be applied to the second adjusting means (119).
  5. Drilling device according to any one of claims 1 to 4,
    characterized in that
    - the first pump control (18) has a first control means (60), to which a first control signal of the setting means (6) can be applied for power limitation and/or power increase of the first hydraulic pump (12) and
    - in that the second pump control (118) has a second control means (160), to which a second control signal of the setting means (6) can be applied for power limitation and/or power increase of the second hydraulic pump (112).
  6. Drilling device according to claim 5,
    characterized in that
    the control signals are electrical, hydraulic and/or pneumatic control signals.
  7. Drilling device according to claim 5 or 6,
    characterized in that
    the setting means (6) is adapted to provide a first control pressure as a first control signal and a second control pressure as a second control signal.
  8. Drilling device according to any one of claims 5 to 7,
    characterized in that
    the setting means (6) is adapted to set the second control signal as a function of the first control signal.
  9. Drilling device according to claim 8,
    characterized in that
    the setting means (6) is adapted to provide at the first and the second pump control (18, 118) control signals of the same magnitude but counter-directional action.
  10. Drilling device according to any one of claims 5 to 9,
    characterized in that
    the setting means (6) is adapted to lower the second control signal in the case
    of an increase of the first control signal and to increase it in the case of a lowering of the first control signal.
  11. Drilling device according to any one of claims 5 to 10,
    characterized in that
    the setting means (6) is adapted to provide identical control signals at the first pump control (18) and the second pump control (118), wherein the control signal acts towards a reduction of the pump power at the first hydraulic pump (12) and towards an increase of the pump power at the second hydraulic pump (112) or vice cersa.
  12. Method for operating a drilling device for soil drilling, in particular according to any one of claims 1 to 11, wherein
    - at least a first hydraulic drive (11) and at least a second hydraulic drive (111) are operated,
    - the first hydraulic drive (11) is supplied with hydraulic fluid by means of a first hydraulic pump (12), which is line-connected with the first hydraulic drive (11), and the second hydraulic drive (111) is supplied with hydraulic fluid by means of a second hydraulic pump (112), which is line-connected with the second hydraulic drive (111),
    - the hydraulic pumps (12, 112) are driven by a common rotation motor (2) and
    - a motor power of the rotation motor (2) is distributed between the first hydraulic pump (12) and the second hydraulic pump (112),
    characterized in that
    - a pump power to be supplied by the first hydraulic pump (12) is controlled by means of a first pump control (18) and a pump power to be supplied by the second hydraulic pump (112) is controlled by means of a second pump control (118) and
    - in that for a different distribution of the motor power of the rotation motor (2) a distribution ratio of the motor power between the first hydraulic pump (12) and the second hydraulic pump (112) is set with an operating element (70).
EP11003342.0A 2011-04-20 2011-04-20 Drilling device Active EP2514911B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
ES11003342T ES2427345T3 (en) 2011-04-20 2011-04-20 Drilling apparatus
PL11003342T PL2514911T3 (en) 2011-04-20 2011-04-20 Drilling device
EP11003342.0A EP2514911B1 (en) 2011-04-20 2011-04-20 Drilling device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11003342.0A EP2514911B1 (en) 2011-04-20 2011-04-20 Drilling device

Publications (2)

Publication Number Publication Date
EP2514911A1 EP2514911A1 (en) 2012-10-24
EP2514911B1 true EP2514911B1 (en) 2013-06-19

Family

ID=44512388

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11003342.0A Active EP2514911B1 (en) 2011-04-20 2011-04-20 Drilling device

Country Status (3)

Country Link
EP (1) EP2514911B1 (en)
ES (1) ES2427345T3 (en)
PL (1) PL2514911T3 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20190096389A (en) * 2016-12-14 2019-08-19 소레탄체 프레씨네트 Excavating Machine with Four Excavating Bodies

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2955315A1 (en) * 2014-06-13 2015-12-16 Sandvik Mining and Construction Oy Rock drilling rig and method of drilling
CN110454140B (en) * 2019-07-22 2022-10-18 中煤科工集团西安研究院有限公司 Drilling machine electro-hydraulic dual-control system with integrated hydraulic linkage valve block and method

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2118650A1 (en) * 1971-04-17 1972-11-02 Salzgitter Maschinen Ag, 3327 Salzgitter-Bad Hydraulic carriage drilling machine for tie rod drilling
US3910358A (en) * 1974-07-05 1975-10-07 Koehring Co Horizontal earth boring machine
CN1162292C (en) * 1997-01-23 2004-08-18 洋马农机株式会社 Moving agricultural machine
DE10051620A1 (en) * 1999-10-18 2001-05-17 Kanzaki Kokyukoki Mfg Co Ltd Tandem pump unit has common housing with first and second openings at opposite ends relative to direction of pump shafts plus separating wall

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20190096389A (en) * 2016-12-14 2019-08-19 소레탄체 프레씨네트 Excavating Machine with Four Excavating Bodies
KR102357851B1 (en) 2016-12-14 2022-02-03 소레탄체 프레씨네트 excavation machine with 4 excavation bodies
US11427985B2 (en) 2016-12-14 2022-08-30 Soletanche Freyssinet Boring machine provided with four boring bodies

Also Published As

Publication number Publication date
EP2514911A1 (en) 2012-10-24
ES2427345T3 (en) 2013-10-30
PL2514911T3 (en) 2013-10-31

Similar Documents

Publication Publication Date Title
EP0856107B1 (en) Output regulation with load sensing
EP0863293B1 (en) Method and apparatus for controlling the push mechanism of an earth drilling rig
DE102013216395B4 (en) CONTROL DEVICE FOR HYDRAULIC ADJUSTING PUMPS AND ADJUSTING PUMP WITH A CONTROL DEVICE
DE102008038435A1 (en) Hydraulic system with an adjustable hydrostatic machine
EP2195560B1 (en) Device for adjusting the stroke volume of hydraulic piston machines
DE2426770B2 (en) HYDRAULIC CONTROL FOR THE FEED AND IMPACT FORCE OF A HYDRAULIC DRILLING MACHINE
EP0149787A2 (en) Feed controlling device for a variable hydropump
EP2006544B1 (en) Piston pump with variable eccentricity
DE3042837A1 (en) CONTROL AND REGULATION DEVICE FOR ADJUSTING THE OUTPUT TORQUE WITH A SUPERVISED LIMIT PERFORMANCE CONTROL IN A HYDROSTATIC TRANSMISSION
EP0825329A2 (en) Drilling apparatus with a feed control device
EP2514911B1 (en) Drilling device
DE102004062388B4 (en) Hydrostatic drive with speed limitation
DE19513032C1 (en) Supply volume setting device for hydraulic pump
DE4020111A1 (en) CONTROL DEVICE FOR SWITCHING A HYDRAULIC SWITCHING MOTOR TO A BASE LOAD MOTOR
EP0745189B1 (en) Device for regulating the total output of at least two hydrostatic variable displacement pumps
DE3321443C2 (en)
EP0561153B1 (en) Capacity regulating device for at least two hydrostatic variable displacement pumps
EP0384888B1 (en) Drilling device
EP2199623A2 (en) Hydraulic system
DE19750367A1 (en) Hydraulic vehicle drive and valve module therefor
EP0211980B1 (en) Driving torque controlling system
DE19742157A1 (en) Control device for an adjustable hydraulic pump with several consumers
DE10006659B4 (en) Control device for a hydraulic pump
WO2011060929A1 (en) Hydraulic assembly comprising a variable displacement pump and a relief valve
DE4140860C2 (en) Control device for a hydrostatic transmission

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20111214

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RIC1 Information provided on ipc code assigned before grant

Ipc: E21B 6/00 20060101AFI20121129BHEP

Ipc: E21B 7/02 20060101ALI20121129BHEP

Ipc: E21B 7/00 20060101ALI20121129BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 617758

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130715

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502011000906

Country of ref document: DE

Effective date: 20130814

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: BOGENSBERGER PATENT- AND MARKENBUERO DR. BURKH, LI

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: NL

Ref legal event code: T3

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2427345

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20131030

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130920

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

REG Reference to a national code

Ref country code: PL

Ref legal event code: T3

REG Reference to a national code

Ref country code: NO

Ref legal event code: T2

Effective date: 20130619

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130919

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131019

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130918

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131021

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

26N No opposition filed

Effective date: 20140320

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011000906

Country of ref document: DE

Effective date: 20140320

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140420

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140420

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20110420

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502011000906

Country of ref document: DE

Representative=s name: WUNDERLICH & HEIM PATENTANWAELTE PARTNERSCHAFT, DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CZ

Payment date: 20180406

Year of fee payment: 8

Ref country code: NO

Payment date: 20180420

Year of fee payment: 8

Ref country code: ES

Payment date: 20180523

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20180424

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20180424

Year of fee payment: 8

REG Reference to a national code

Ref country code: NO

Ref legal event code: MMEP

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20190420

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190420

Ref country code: NO

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190430

Ref country code: CZ

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190420

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190421

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20200831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190421

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190420

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230505

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20230417

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20230428

Year of fee payment: 13

Ref country code: FR

Payment date: 20230417

Year of fee payment: 13

Ref country code: DE

Payment date: 20230426

Year of fee payment: 13

Ref country code: CH

Payment date: 20230502

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20230414

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20230417

Year of fee payment: 13