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EP2514911B1 - Appareil de forage - Google Patents

Appareil de forage Download PDF

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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
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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
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German (de)
English (en)
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EP2514911A1 (fr
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 EP11003342.0A priority Critical patent/EP2514911B1/fr
Priority to ES11003342T priority patent/ES2427345T3/es
Priority to PL11003342T priority patent/PL2514911T3/pl
Publication of EP2514911A1 publication Critical patent/EP2514911A1/fr
Application granted granted Critical
Publication of EP2514911B1 publication Critical patent/EP2514911B1/fr
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK 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 OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK 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 OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK 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 characterised 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.

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  • Life Sciences & Earth Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (12)

  1. Appareil de forage pour forer le sol, avec
    - au moins un premier entraînement hydraulique (11) et au moins un deuxième entraînement hydraulique (111),
    - au moins une première pompe hydraulique (12) et au moins une deuxième pompe hydraulique (112) qui, en vue d'un transfert d'énergie au moyen d'un fluide hydraulique, sont raccordées au premier entraînement hydraulique (11), respectivement au deuxième entraînement hydraulique (111), et
    - un moteur rotatif (2) avec un arbre de sortie (4) sur lequel, pour délivrer une puissance moteur déterminée, s'applique un couple de rotation par lequel la première pompe hydraulique (12) et la deuxième pompe hydraulique (112) sont entraînées, la puissance moteur du moteur rotatif (2) étant répartie entre la première pompe hydraulique (12) et la deuxième pompe hydraulique (112),
    caractérisé en ce que
    - une première commande de pompe (18) et une deuxième commande de pompe (118) sont prévues pour piloter la puissance de pompe à délivrer par la première pompe hydraulique (12), respectivement par la deuxième pompe hydraulique (112),
    - en ce qu'un dispositif de réglage (6) est prévu pour régler différentes répartitions de la puissance moteur du moteur rotatif (2) entre la première pompe hydraulique (12) et la deuxième pompe hydraulique (112), et
    - en ce que le dispositif de réglage (6) présente un élément de commande (70) avec lequel un rapport de répartition de la puissance moteur du moteur rotatif (2) entre la première pompe hydraulique (12) et la deuxième pompe hydraulique (112) peut être réglé.
  2. Appareil de forage selon la revendication 1, caractérisé en ce que les commandes de pompe (18, 118) des pompes hydrauliques (12, 112) sont conformées pour une régulation de puissance de la première pompe hydraulique (12), respectivement de la deuxième pompe hydraulique (112).
  3. Appareil de forage selon la revendication 1 ou 2, caractérisé en ce que
    - la première commande de pompe (18) présente un premier dispositif de manoeuvre (19) et la deuxième commande de pompe (118) un deuxième dispositif de manoeuvre (119),
    - en ce que le premier dispositif de manoeuvre (19) est conformé pour instaurer un débit de transport de la première pompe hydraulique (12) en fonction d'une pression de travail dans une conduite pressurisée (14) de la première pompe hydraulique (18), et
    - en ce que le deuxième dispositif de manoeuvre (119) est conformé pour instaurer un débit de transport de la deuxième pompe hydraulique (112) en fonction d'une pression de travail dans une conduite pressurisée (114) de la deuxième pompe hydraulique (112).
  4. Appareil de forage selon la revendication 3, caractérisé en ce que
    - le premier dispositif de manoeuvre (19) peut être chargé avec une première pression de manoeuvre correspondant à la pression de travail de la première pompe hydraulique (12), et
    - en ce que le deuxième dispositif de manoeuvre (119) peut être chargé avec une deuxième pression de manoeuvre correspondant à la pression de travail de la deuxième pompe hydraulique (112).
  5. Appareil de forage selon l'une des revendications 1 à 4, caractérisé en ce que
    - la première commande de pompe (18) présente un premier dispositif de commande (60) qui, en vue d'une limitation de puissance et/ou d'une élévation de puissance de la première pompe hydraulique (12), peut être chargé avec un premier signal de commande du dispositif de réglage (6), et
    - en ce que la deuxième commande de pompe (118) présente un deuxième dispositif de commande (160) qui, en vue d'une limitation de puissance et/ou d'une élévation de puissance de la deuxième pompe hydraulique (112), peut être chargé avec un deuxième signal de commande du dispositif de réglage (6).
  6. Appareil de forage selon la revendication 5, caractérisé en ce que les signaux de commande sont des signaux de commande électriques, hydrauliques et/ou pneumatiques.
  7. Appareil de forage selon la revendication 5 ou 6, caractérisé en ce que le dispositif de réglage (6) est aménagé pour délivrer, comme premier signal de commande, une première pression de commande et, comme deuxième signal de commande, une deuxième pression de commande.
  8. Appareil de forage selon l'une des revendications 5 à 7, caractérisé en ce que le dispositif de réglage (6) est aménagé pour régler le deuxième signal de commande en fonction du premier signal de commande.
  9. Appareil de forage selon la revendication 8, caractérisé en ce que le dispositif de réglage (6) est aménagé pour délivrer à la première et à la deuxième commande de pompe (18, 118) des signaux de commande de même taille, mais agissant en sens opposé.
  10. Appareil de forage selon l'une des revendications 5 à 9, caractérisé en ce que le dispositif de réglage (6) est aménagé pour abaisser le deuxième signal de commande en cas d'élévation du premier signal de commande et à l'élever en cas d'abaissement du premier signal de commande.
  11. Appareil de forage selon l'une des revendications 5 à 10, caractérisé en ce que le dispositif de réglage (6) est aménagé pour délivrer des signaux identiques à la première commande de pompe (18) et à la deuxième commande de pompe (118), le signal de commande agissant sur la première pompe hydraulique (12) dans le sens d'une réduction de la puissance de pompe et sur la deuxième pompe hydraulique (112) dans le sens d'une augmentation de la puissance de pompe, ou inversement.
  12. Procédé d'exploitation d'un appareil de forage pour forer le sol, en particulier selon l'une des revendications 1 à 11, dans lequel
    - au moins un premier entraînement hydraulique (11) et au moins un deuxième entraînement hydraulique (111) sont utilisés,
    - le premier entraînement hydraulique (11) est alimenté en fluide hydraulique au moyen d'une première pompe hydraulique (12) qui est raccordée au premier entraînement hydraulique (11) et le deuxième entraînement hydraulique (111) est alimenté en fluide hydraulique au moyen d'une deuxième pompe hydraulique (112) qui est raccordée au deuxième entraînement hydraulique (111),
    - les pompes hydrauliques (18, 118) sont entraînées par un moteur rotatif (2) commun, et
    - une puissance moteur du moteur rotatif (2) est répartie entre la première pompe hydraulique (12) et la deuxième pompe hydraulique (112),
    caractérisé en ce que
    - une puissance de pompe devant être délivrée par la première pompe hydraulique (12) est commandée au moyen d'une première commande de pompe (18) et une puissance de pompe devant être délivrée par la deuxième pompe hydraulique (112) est commandée au moyen d'une deuxième commande de pompe (118), et
    - en ce que, pour une répartition variable de la puissance moteur du moteur rotatif (2), un rapport de répartition de la puissance moteur entre la première pompe hydraulique (12) et la deuxième pompe hydraulique (112) est réglé avec un élément de commande (70).
EP11003342.0A 2011-04-20 2011-04-20 Appareil de forage Active EP2514911B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP11003342.0A EP2514911B1 (fr) 2011-04-20 2011-04-20 Appareil de forage
ES11003342T ES2427345T3 (es) 2011-04-20 2011-04-20 Aparato de perforación
PL11003342T PL2514911T3 (pl) 2011-04-20 2011-04-20 Urządzenie wiercące

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11003342.0A EP2514911B1 (fr) 2011-04-20 2011-04-20 Appareil de forage

Publications (2)

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

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ID=44512388

Family Applications (1)

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EP11003342.0A Active EP2514911B1 (fr) 2011-04-20 2011-04-20 Appareil de forage

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20190096389A (ko) * 2016-12-14 2019-08-19 소레탄체 프레씨네트 4개의 굴착 몸체를 갖는 굴착 기계

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2955315A1 (fr) * 2014-06-13 2015-12-16 Sandvik Mining and Construction Oy Appareil de forage de roches et procédé de forage
CN110454140B (zh) * 2019-07-22 2022-10-18 中煤科工集团西安研究院有限公司 具备集成式液压联动阀块的钻机电液双控制系统及方法

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2118650A1 (de) * 1971-04-17 1972-11-02 Salzgitter Maschinen Ag, 3327 Salzgitter-Bad Hydraulische Lafetten-Bohrmaschine für das Zugankerlochbohren
US3910358A (en) * 1974-07-05 1975-10-07 Koehring Co Horizontal earth boring machine
KR100516665B1 (ko) * 1997-01-23 2005-12-14 얀마-노키 가부시키가이샤 이동농기
US6487856B1 (en) * 1999-10-18 2002-12-03 Kanzaki Kokyukoki Mfg. Co., Ltd. Tandem pump unit

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20190096389A (ko) * 2016-12-14 2019-08-19 소레탄체 프레씨네트 4개의 굴착 몸체를 갖는 굴착 기계
KR102357851B1 (ko) 2016-12-14 2022-02-03 소레탄체 프레씨네트 4개의 굴착 몸체를 갖는 굴착 기계
US11427985B2 (en) 2016-12-14 2022-08-30 Soletanche Freyssinet Boring machine provided with four boring bodies

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