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    • 专利摘要:
    SUMMARY A sink drill, which includes a drill bit (40), a reciprocating piston (20), operable to provide a shock load on the drill bit, and means for changing the frequency with which the piston delivers a shock load to the drill bit, also resulting in a change in the total effect for the benefit. The means for changing the frequency and the total power can be maneuvered during continuous operation of the bee. The means for changing the frequency and the total power may optionally include a valve (130) for selectively changing the effective volume of a drive or return chamber, an actuator (140) for changing the timing of setting the drive (25) or return chamber. (30) in connection with the blow-out (95), or a system for changing the frequency in response to the sensing of a predetermined drift parameter flitbone, such as the pressure or the position of the piston.
    公开号:SE537971C2
    申请号:SE1151155
    申请日:2010-05-05
    公开日:2015-12-22
    发明作者:Timothy J Plunkett；Dale R Wolfer；Paul Campbell
    申请人:Atlas Copco Secoroc Llc；
    IPC主号:
    专利说明:

    SUMMARY A sink drill, which includes a drill bit (40), a reciprocating piston (20), operable to provide a shock load on the drill bit, and means for changing the frequency with which the piston delivers a shock load to the drill bit, also resulting in a change in the total effect for the benefit. The means for changing the frequency and the total power can be maneuvered during continuous operation of the bee. The means for changing the frequency and the total power may optionally include a valve (130) for selectively changing the effective volume of a drive or return chamber, an actuator (140) for changing the timing of setting the drive (25) or return chamber. (30) in connection with the blow-out (95), or a system for changing the frequency in response to the sensing of a predetermined drift parameter flitbone, such as the pressure or the position of the piston.
    TECHNICAL FIELD The present invention relates to a submersible drilling rig and a method for operating a submersible drilling rig.
    BACKGROUND OF THE INVENTION When drilling in a soil formation, the previous edge is that one can feed a number of parameters or quantities into the drill tail, e.g. in oil shells, with the help of various sensors placed in a unit down in the tail. The data generated from the sensors can be stored in a memory provided in the unit down in the tail, or they can also be coded and transmitted to the surface via some kind of transmission system. For an operator, it is advantageous to receive this data at the surface.
    Document GB 2236782 describes a method for transmitting data from sensors near one called the bottom. The method comprises converting the signals from the sensors into the form of binding numbers, and transmitting them in the form of acoustic signals is lengthened by the drill string to a receiver at the drilling rig. By using several hammers, arranged to hit the drill string in sequence, the data delivery speed is improved. The harnesses may optionally be arranged to strike one or more peripheral flange shears on the drill string.
    Document WO 9919751 describes a communication rod for the drill rod for transmitting data between locations in a downhole and the surface, which comprises at least one transducer at a first location on a drill rod for modulating the movement and / or stress in the drill rod, and at least one transducer at a second place on the drill rod for detecting the modulation. Control units may optionally be provided at both sites for establishing communication between the sites.
    The disadvantages of the prior art solutions are that drilling must be interrupted during data transfer, or at least interrupted to enable a data transfer at an acceptable quality level. These interruptions are time-consuming and result in increased costs for the drilling operations.
    There is thus a need for improved efficiency and reliability in sink drilling. The state of the art technology does not meet these needs.
    SUMMARY OF THE INVENTION An object of the present invention is to provide a submersible drilling rig with improved performance. The problem to solve is to eliminate the limitation in the control of a sinker to drive performance and thus increase the reliability for customers.
    The solution according to the invention provides a sink drill with variable frequency.
    According to a first aspect of the present invention, there is provided a submersible drilling assembly comprising a supply of propellant fluid, in the form of compressible fluid, a drill bit, a blowout structure communicating through the drill bit with the atmosphere, a reciprocating piston with forward and reciprocating motion with respect to pa borrkronan. The sink drill assembly is further characterized by a drive chamber above the piston and a return chamber below the piston. The drilling assembly further comprises means for driving the reciprocating motion of the piston by alternately connecting the drive chamber in connection with the supply of drive fluid and the return chamber in connection with the blow-out structure in a first instance, and in connecting the drive chamber in connection with the blow-out structure and return chamber. the supply of propellant fluid in a second instance. The submersible drilling rig also includes a sensor and a control unit for generating a command signal and means for changing, in response to the command signal and 2 maneuvering via the control unit, the frequency with which the piston delivers shock load to the drill bit, the sensor and the means for changing the frequency the drilling rig is down in the drill fillet.
    This is achieved in a submersible drilling tool which is capable of generating data, which data is presented to the operator in real time. Accordingly, the present invention provides a real-time control of a submersible drilling tool. 2 All embodiments described below are considered useful for oil and gas drilling applications, mining applications and deep neck applications / geothermal applications.
    The invention includes several embodiments that demonstrate different means and methods for changing frequency. The present invention can be used for the second frequency of drilling operation during continuous operation of the drill, without having to remove the drill from the hall in which it operates and without having to cease drilling operation.
    In one embodiment, the frequency of the piston struts on the striking surface of the drill bit is detected by feeding above ground of the frequency of seismic waves, i.e. vibrations transmitted in the earth, provided by the pistons of the piston. In another embodiment, the frequency of the piston struts on the striking surface of the drill bit is detected by feeding above ground the frequency of vibrations transmitted and propagated along a drill string provided by the piston struts.
    In certain embodiments, the frequency change means includes means for changing the frequency during continuous operation of the drill. In some embodiments, the frequency change means comprises a chamber with an additional volume and a valve, maneuverable via the control unit between an open position in which the valve salts the drive chamber in connection with the chamber with an additional volume, and a closed state in which the valve shuts off the connection between the additional volume chamber and the drive chamber. In some embodiments, the frequency change means comprises a chamber with an additional volume and a valve, operable via the control unit between an open position, in which the valve puts the return chamber in communication with the chamber with an additional volume, and a closed state, in which the valve switches off the connection between the additional volume chamber and the return chamber. In some embodiments, the means for changing the frequency includes an actuator manoeuvrable via the control unit for changing the time when the drive chamber is connected to the blow-out structure. In certain embodiments, the means for changing the frequency comprises an actuator manoeuvrable via the control unit for changing the time when the drive chamber is salted in connection with the supply of drive fluid. In certain embodiments, the means for changing the frequency includes an actuator maneuverable via the control unit for changing the time when the return chamber is connected to the blow-out structure. In some embodiments, the means for changing the frequency includes an actuator operable via the control unit for changing the time when the return chamber is connected to the supply of drive fluid. In some embodiments, the variable frequency sink further comprises a control system for sensing an operating parameter of the drill and maneuvering the means for changing the frequency in response to the sensing of a predetermined operating parameter. In some embodiments, the control system includes a control unit and a sensor that senses one of the position of the pressure and the piston. In some embodiments, the sensor is located in the drill bit or between the drill bit and the drill string. In some embodiments, the sensor is located near the drill bit. In some embodiments, the control system includes a control unit, a control valve, and a main valve; wherein the main valve opens in response to a lifting pressure obtained in the drive chamber for communicating the drive chamber with the supply of drive fluid; and wherein the control unit opens the control valve for generating a control signal from the control valve to the main valve to delay the opening of the main valve after the lifting pressure has been reached, for the second time of the opening of the main valve.
    In some embodiments, the means for driving the reciprocating motion of the piston includes a valve, and the means for changing the frequency includes a mechanism for changing the timing of operation of the valve.
    In some embodiments, the mechanism for changing the timing of operation of the valve is maneuverable during continuous operation of the drill. In some embodiments, the mechanism for changing the timing of operation of the valve includes a second valve, operable to open and close the connection between one of the drive and return chambers and a chamber with an additional volume. In some embodiments, the mechanism for changing the timing of operation of the valve includes a mechanism for changing the timing of contacting at least one of the drive chamber and the return chamber with at least one of the feed fluid supply and exhaust structure. In some embodiments, the mechanism includes changing the timing of operation of the valve to a sensor that monitors an operating parameter of the drill and generating the command signal in response to sensing a predetermined value of the operating parameter. In some embodiments, the sensor is located in the drill bit or between the drill bit and the drill string. In some embodiments, the sensor is located near the drill bit. In some embodiments, the mechanism for changing the timing of operation of the valve includes a control unit, a control valve and a main valve; wherein the main valve opens in response to a lifting pressure obtained in the drive chamber to connect the drive chamber to the supply of drive fluid; and wherein the control unit opens the control valve to generate a control signal from the control valve to the main valve to delay the opening of the main valve after the lifting pressure has been reached, for the second time of the opening of the main valve.
    According to a second aspect of the present invention there is provided a method of operating a sink drill at variable speeds, the method comprising: (a) driving the reciprocating motion of a piston by alternately establishing and shutting off the connection between a feed fluid drive in the form of compressible fluid and blowout and opposite spirits of the piston when the drill assembly is down in the drill tail; (b) striking a drill bit with the piston once per operating cycle of the piston; and (c) during continuous operation of the drill, changing a time at which the connection between at least one of the opposite spirits of the piston and at least one of the supply of propellant fluid and the blowout is established and shut off.
    In some embodiments, step (c) involves sensing an operating parameter of the drill during continuous operation of the drill, which automatically generates a conunando signal in response to the operating parameter corresponding to a predetermined value, and, in response to generating the command signal, operating a mechanism for changing the timing of the connection between at least one of the opposite spirits of the piston and at least one of the supply of propellant fluid and the exhaust.
    Other aspects of the invention will become apparent upon consideration of the detailed description and accompanying drawings.
    BRIEF DESCRIPTION OF THE DRAWINGS Figures 1-6 are a schematic illustration of a first embodiment of the invention operating at a first frequency. Figures 7-8 are a schematic illustration of the first embodiment operating at a second frequency. Figures 9-are a schematic illustration of a second embodiment of the invention operating at a first frequency, Figures 11-12 are a schematic illustration of the second embodiment operating at a second frequency. Figures 13-14 are a schematic illustration of a third embodiment of the invention operating at a first frequency. 15-16 is a schematic illustration of the third embodiment operating at a second frequency, Figure 17 is a schematic illustration of the third embodiment during a drive stroke portion of the cycle, Figure 18 is a schematic illustration of a fourth embodiment of the invention at a moment in a return stroke, during which a drive compartment is closed, Figures 19-one schematic illustration of the fourth embodiment operating at a first frequency, Figures 21-22 are a schematic illustration of the fourth embodiment operating at a second frequency, and Figure 23 is a schematic illustration of the fourth embodiment during a drive stroke part of the cycle.
    Figure 24 is a schematic illustration of an alternative embodiment.
    Figure is a schematic illustration of an alternative embodiment. Figure 26 is a schematic illustration of an alternative embodiment.
    DETAILED DESCRIPTION Before any embodiments of the invention are explained in detail, it will be appreciated that the invention in its application is not limited to the constructional details and arrangements of components disclosed in the description which follows or illustrated in the accompanying drawings. The invention is capable of other embodiments and of being practiced or of being carried out in various ways.
    Figure 1 schematically illustrates a sankbon assembly 10 including a housing 15, a piston 20, a drive gun 25 above the piston 20, a return chamber 30 below the piston 20, a feed chamber 35 between the drive chamber 25 and the return chamber 30 and a drill bit 40. The piston 20 moves back and forth in the housing 15 for applying shock loads to the drill bit 40.
    The housing 15 defines a longitudinal axis 45 which is substantially vertical in the normal operating orientation of the drill. In the schematic drawings, the housing 15 includes a feed portion 6 having a first inner diameter, a drive side portion 55 having a second inner diameter larger than the first inner diameter and the return side portion 60 having a third inner diameter which is also stone of the first inner diameter. The third inner diameter is illustrated as approximately equal to the second inner diameter, but in reality the second and third inner diameters may be different. Furthermore, in some embodiments, the first inner diameter may in fact be stepped and have several diameters. The transition from the feed portion 50 to the drive side portion 55 defines a drive step 65 and the transition from the feed portion 50 to the return side portion 60 defines a return step 70.
    The piston 20 includes a center portion 75 having a first outer diameter, an upper portion 80 and a lower portion 85. The upper portion 80 and the lower portion 85 have outer diameters of stone on the first outer diameter. The schematic drawings illustrate the upper part 80 and the lower part 85 as having equal outer diameters, but in reality the upper part 80 and the lower part 85 may have different outer diameters. A center bore 90 extends through the piston 20 in the longitudinal direction.
    An exhaust duct 95 communicates through the drill bit 40 to atmospheric pressure. Drive fluid flows out of the exhaust duct 95 and flushes cuttings and other debris from around the drill bit 40 and further up through the hE in which the drill operates. A plug 100 extends 20 into the drive chamber 25. In other embodiments, the plug 100 may include a drive feed channel for feeding drive fluid to the feed chamber 35, but such a feed channel functionally includes an element that selectively extends into the central bore 90 as well as the plug 100 Or the schematically illustrated embodiment. The exhaust duct 95 and the plug 100 have outer diameters approximately equal to the diameter of the central bore 90 and are in line with the central bore 90.
    The reciprocating motion of the piston 20 is driven by propellant fluid (e.g., a compressible fluid such as air or an incompressible fluid such as hydraulic oil) provided to the feed portion 50 of the housing 15 from a cold to propellant fluid 105. 105 is shown communicating directly with the feed chamber 35 through the side of the housing 15, in most commercial embodiments the source of drive fluid 105 provides drive fluid to the feed chamber 35 through a drill or drill string connecting to the top of the drill assembly 10 (i.e. communicating with the feed channel / plug 100 discussed). above and 7 ported to the feed chamber 35). Although the drive fluid in the schematically illustrated embodiment flows into a feed chamber 35 which is physically located between the drive chamber 25 and the return chamber 30, the scope of the invention is not limited by such a physical arrangement. There are many other porting and air logic arrangements in which the drive fluid can be alternated between the drive chamber 25 and the return chamber 30 to open. the functionality described below.
    Referring to Figure 1, as the upper portion 80 of the piston 20 moves free from the drive stage 65, the drive chamber 25 is set free, substantially at the same time as the upper part 80 of the piston 20 or free from the drive stage 65 is opened and closed several other connections: the lower part 85 of the piston 20 registers with the return stage 70 to switch off the connection between the return chamber 30 and the feed chamber 35; the exhaust duct 95 is removed from the central bore 90 to open the connection between the return chamber 30 and the exhaust; and the plug 100, it is accepted that the central bore 90 is allowed to extend by the connection between the drive chamber 25 and the central bore 90. In other embodiments, the connections mentioned above may occur in offset progression rather than substantially simultaneously. For example, the plug 100 may be accepted in the central bore 90 before the exhaust duct 95 is removed from the central bore 90 and before the upper part 80 of the piston 20 is released from the drive stage 65.
    Referring to Figure 2, as the piston 20 continues to rise, pressure builds up rapidly in the drive chamber 25 ph due to drive fluid rushing to the drive chamber 25 simultaneously with the decreasing volume of the drive chamber 25 due to the upward movement of the piston 20. In the drawings, the tightness of the puncture is roughly proportional to the pressure.
    The rise in pressure stops the upward movement of the piston 20 and drives the piston downwards against a bump with the drill bit 40 again. The pressure in the drive chamber 25 at which the rising motion of the piston 20 is stopped is referred to throughout this description as the "critical pressure". The initial downward movement of the piston 20 is not significantly resisted, as residual driving fluid in the return chamber 30 is vented through the exhaust passage 95 (as illustrated by the return exhaust arrows 110).
    In Figure 3, the piston 20 is in the middle of its kind and the connection between the supply of drive fluid is temporarily disconnected from both the drive chamber 25 and the return chamber 30. In Figure 4, the feed chamber 35 is set, as the lower part 85 of the piston 20 leaves the return stage 70. in connection with the return chamber 30. substantially at the same time as the lower part 85 of the piston 20 leaves the return stage 70, several other connections are opened and closed: the upper part 80 of the piston 20 registers with the drive stage 65 to switch off the connection between the drive chamber 25 and the feed chamber 35; the exhaust duct 95 is accepted within the central bore 90 to shut off the connection between the return chamber 30 and the exhaust; and the plug 100 is removed from the central bore 90 to open the connection between the drive chamber 25 and the exhaust through the central bore 90 and the exhaust duct 95. As discussed above with respect to the upward stroke of the piston 20, the timing of these connections may be offset and not usually simultaneously in all embodiments. Since the interaction between the piston 20, the drive stage 65, the return stage 70, the center bore 90, the blow-out channel 95 and the plug 100 controls the communication of the drive chamber 25 and the return chamber 30 with the supply of drive fluid 105 and with the blow-out, the unit can be referred to as a valve.
    Now referring to Figures 5 and 6, drive fluid rushes to the return chamber 30 as drive fluid rushes out of the drive chamber 25 and is blown out through the drill bit 40 to the atmosphere (as illustrated by the drive blow-out arrows 115). Pressure builds up rapidly in the return chamber 20 as its volume decreases due to the downward movement of the piston 20, but there is sufficient downward impulse in the piston 20 to make it possible for it to hit the drill bit 40, which transfers the impact load to the rock or other substrate to be drilled. As pressure builds up rapidly and is assisted by the piston 20 of the drill bit 40, the piston 20 is driven up. The initial upward movement of the piston 20 is not significantly resisted by pressure in the drive chamber 25, since any drive fluid in the drive chamber 25 is blown out through the central bore 90 and the exhaust duct 95 (see the drive blow-out arrows 115).
    In Figures 1-6, described above, the drill operates at a first frequency. For the purposes of this disclosure, the term "drill frequency" and similar terms refer to the frequency with which the piston 20 provides a shock load on the drill bit 40. There are several ways of referring to the frequency of the second drill. The impact frequency of the piston 20 on the drill bit 40 has an inverse relationship with the stroke of the piston 20, so that an increase in stroke results in a decrease in the frequency of the drill. The stroke of the piston 20 is set in part by the volume of the drive chamber 25. The piston 20 stops rising, as the force on the piston 20 from the pressure in the drive chamber 25 is sufficient to overcome the upward impulse of the piston 20. The pressure is a function of the volume, since all other factors (such as temperature) remain essentially constant. Therefore, if the volume of the drive chamber 25 is expanded, the piston 20 is allowed to rise higher before the pressure reaches a level sufficient to stop the upward impulse of the piston 20. As a result, the frequency of the drill, with other factors being substantially constant, will decrease as the volume of the drive chamber 25 increases.
    The frequency of the drill can awn correlate with the impact load provided by the piston 20 on the drill bit 40 in each cycle. In general, a drill operating at a higher frequency, with all other factors (eg volumes and feed pressure for propellant fluid) will be substantially constant, will provide lower impact load on the drill bit in each cycle and a drill operating at a lower frequency will also provide higher shock load per bicycle. Impact load per bicycle in combination with the frequency of operation determines the total power of the hammer.
    Typically, an actuator with a high frequency, low impact load per cycle will result in a lower total handling power and an actuator with a law-equivalent, high impact load per cycle will again result in a higher total hammer effect. The present invention allows a hammer to operate in the earlier mode (with high frequency, low impact load) when drilling in comparatively soft substrates and in the latter mode (with low frequency, high impact load) when drilling in comparatively hard substrates. In addition, the present invention may make it possible to reduce the risk of drill bit failure by operating at a total drilling power suitable for the substrate to be drilled and the conditions for the weight of the drill bit in the tail. In view of the interplay between the drilling frequency and the total effect, it should be understood that male references to changes in the drilling frequency implicitly include the resulting changes in the nest effect.
    The impact from the piston 20 on the drill bit 40 generates seismic vigors through the ground or vibrations through the drill and drill pipe, which can be read at the surface with geophones or other sensors, or with accelerometers or other frequency or speed feeders or monitors on the drilling rig. One may wish for the frequency of the second drill to convey information to the surface. Sequences of change in frequency can be used as a code and the sequences can be decoded at the surface to experience the operating conditions at the bottom of the tail to be drilled. If the frequency of the drill can be changed during operation (eg "in the cases"), information can be transmitted to the surface without having to stop the drilling operation. The present invention allows the transmission of information during drilling operation, where the only change in operation is a change in frequency and not a complete cessation. Terms such as "in operation" are meant to mean that a change in frequency can occur without removal of the drill assembly from Met so that manual adjustments can be made to the drill assembly to increase the frequency of the second drill.
    Figures 7 and 8 illustrate a first mechanism for selectively increasing the volume of the drive chamber 25 to consequently increase the stroke and reduce the frequency of the drill. The drill is equipped with sensors 120 to detect one or more potentially relevant environmental factors such as temperature, radiation, magnetic field, earth magnetic field vector, direction of gravity and drill bit weight. The sensor 120 in the illustrated embodiment is mounted on the drill bit 40, but other sensors 120 may be positioned elsewhere in the drill assembly, depending on what the sensors 120 are designed to sense.
    These sensors 120 transmit or generate (via wired or wireless means) command signals to a control unit 125, which may be physically mounted on the drill assembly 10. The control unit 125 communicates with and controls the operation of a valve 130, which is also mounted on the drill assembly. In other embodiments, the control unit 125 may be part of a control unit at the surface, which receives information from the sensors 120 by some appropriate means and which is manually operable by an operator at the surface.
    The valve 130 is manoeuvrable between an open position, in which the valve 130 sanitizes the drive chamber 25 in connection with a gun with an additional volume 135, and a closed state, in which the valve 130 shuts off the connection between the chamber with an additional volume 135 and the drive chamber 25. When the valve 130 is in the closed state, the drive chamber 25 has a first volume, and when the valve 130 is in the open state, the drive chamber has a second effective volume (larger than the first volume), which includes the original volume of the chamber 25 plus the volume of the few chambers with a additional volume 135.
    Referring specifically to Figures 7 and 8, when the controller 125 receives a command signal from the sensor 120 requiring the controller 125 to send information to the surface, the controller 125 automatically drills the frequency in a predetermined sequence by opening 11 and closing the valve 130. In other embodiments an operator at the surface can maneuver the control unit 125 after receiving the command signal from the sensor 120. With the valve 1-rod, the drill operates as described above with respect to Figures 1-6 and at a first frequency. With the valve 130 open, the effective volume of the drive chamber 25 is increased to the original volume plus the additional volume 135. As a result, the piston 20 rises higher before its upward impulse is stopped (ie before it reaches critical pressure; see Figure 8), which increases the stroke for piston 20 and reduces the frequency of the drill.
    Figures 9-12 illustrate another arrangement for changing the frequency of the drill. In this arrangement, the control unit 125 drives an actuator 140 which is connected to the plug 100.
    The control unit 125 changes the frequency of the drill by moving the plug 100 longitudinally or axially (ie along the shaft 45) so that at the second time, the plug 100 stops and opens the connection between the drive chamber 25 and the center bore 90. With the actuator 140 in a first state (e.g. at rest or retracted), illustrated in Figures 9 and 10, the piston 20 rises to a first WO before the critical pressure is reached in the drive chamber 25 to stop the upward impulse of the piston 20. In Figures 11 and 12, the control unit 125 has received a signal from the sensor 120 and has actuated the actuator 140 to a second condition (eg projecting), so that the plug 100 moves neatly along the longitudinal axis 45 towards the drill bit 40. This results in the connection between the drive chamber 25 and the center bore 90 being switched off earlier in the uptake. the stroke of the piston 20, which results in the pressure building up faster in the drive chamber 25 so that the critical pressure is reached earlier (i.e. at a bearing 1 16.0 for the piston 20) in Figures 9 and 10. As a result, the upward impulse of the piston 20 is stopped earlier (the stroke is reduced) and the frequency of the drill is equalized. Of course, in other embodiments, the actuator 140 could be configured to operate normally in the advanced condition, illustrated in Figures 11 and 12, and selectively maneuvered to the retracted condition, illustrated in Figures 9 and 10, to increase the stroke and reduce the frequency of the drill.
    Figures 13-17 illustrate another alternative control arrangement 210 that includes a control valve 215 and a main valve 220. In this embodiment, the call to drive fluid 105 communicates with the main valve 220 through a primal. channel 225 and communicates with the control valve 215 through a secondary channel 230. A control channel 235 communicates between the control valve 215 and the main valve 220, and a supplementary supply channel 12 communicates between the main valve 220 and the drive chamber 25. The supply pressure acting on the main valve 220 through the control channel 235 may be as a pilot signal or control signal. The control unit 125 opens and closes the control valve 215 electronically (via wired or wireless means) to turn on the respective rod of the control signal. The control valve 215 may in certain embodiments include a suitable electromechanical unit, such as a solenoid, which converts the electronic control signals from the control unit 125 to turn on and off the control signal.
    The main valve 2 may optionally be configured as a differential valve, with pressure from the supplemental supply channel 240 acting on a first surface area 250 of the valve 220, pressure from the primary channel 225 acting on a second surface area 255 (facing substantially in the opposite direction to the first surface area 250) and the control signal from the control channel 235 which acts on a third surface area 260 (which also faces substantially in the opposite direction to the first surface area 250). In an arrangement of surface areas, the force generated by the critical pressure in the drive chamber 25 acting on the first surface area 250 is insufficient to overcome the combined forces of the feed pressure acting on the second and third surface areas 255, 260 and the main valve 220 remains closed as long as provided by the control signal. When the control signal is turned off, however, the force of the pressure in the drive chamber 25 acting on the first surface area 2 overcomes the force of the supply pressure of the second surface area 255 before the pressure in the drive chamber 25 reaches the critical pressure, causing the main valve 220 to open.
    The pressure in the drive chamber 25 which is necessary to open the main valve 220 can be referred to as "lifting pressure", and is proportional to the size of the second surface area 255 for a given first surface area 250. In some forms it is undesirable for the second surface area 25 to be small. so that the lift pressure is rapidly reached in the absence of the control signal acting on the third surface area 260. Once the lift pressure is reached and the main valve 220 opens, driving fluid flows to the drive chamber 25 through the main valve 220 and the supplemental supply channel 240.
    Figures 13 and 14 illustrate the drill operating at a first frequency. In these figures, the control unit 125 opens the control valve 215 to generate the control signal, which effectively lasers the main valve 220 in a closed position. As a result, the drill in Figures 13 and 14 described with respect to Figures 1-6 operates. Figure 13 illustrates the feed chamber 35 connected to the drive chamber 25 for increasing the pressure in the drive chamber 25, and Figure 14 illustrates that the critical pressure has been reached in the drive chamber 25 without opening the main valve 220.
    Figures -17 illustrate the drill operating at a second frequency which is higher than the first frequency. In these figures, the control unit 125 initially shuts off the control valve 215 to turn off the control signal. Referring to Figure 15, the main valve 220 (e.g., the balance between the first, second and third surface areas 250, 255, 260) is arranged so that the pressure in the drive chamber 25 at the lifting pressure before the upper portion 80 of the piston 20 is released from the shoulder 65, the main valve 220 opens and drive fluid is forced into the drive chamber 25. During reference to Figure 16, critical pressure is gained more quickly as a result of the main valve 220 opening in Figure 14, in which the main valve 220 is held closed. Consequently, the stroke is shortened and the frequency of the drill, dA, is increased. the control valve 215 is closed.
    Despite the early introduction of drive fluid into the drive chamber 25, the upward impulse of the piston 20 causes the bottom 85 of the piston 20 to release from the exhaust duct 95 before the critical pressure is reached in the drive chamber 25, and the drive fluid in the return chamber 30 is rapidly vented as the piston 20 downward battle. Referring to Figure 17, the pressure in the drive chamber 25 falls below the lift pressure rapidly after the plug 100 is removed from the piston bore 90, causing the main valve 220 to return. to the closed position 20 because the force exerted by the feed pressure acting on the second surface area 255 exceeds the force exerted by the reduced (eg substantially atmospheric) pressure acting on the first surface area 250.
    Figures 18-23 illustrate another embodiment 310 of a control system having a variable frequency drill. In this embodiment there is no drive shaft 65, but there is a return shaft 70. This embodiment also includes a sensor 315 in the drive chamber 25 or on the piston 20 which senses a real-time operating parameter of the drill, such as the pressure of the drive chamber or the position of the piston. Figure 18 illustrates the point in the return stroke when the plug 100 closes the piston bore 90. The control unit 125 has received the control valve 215 sA. aft control signal effectively laser main valve 220 in rod brine. Continued upward movement of the piston 20 from the position illustrated in Figure 18 causes an increase in pressure in the drive chamber 25 due to the resulting reduced volume. Figures 19 and 20 illustrate an extreme of the operation of the control system 310, in which the control unit 125 closes the control valve 215 after the piston 20 reaches the position illustrated in Figure 18, so that the main valve 220 is allowed to open after the pressure in the drive chamber 25 reaches the lifting pressure. The configuration of the first, second and third surface areas 250, 255, 260 of the main valve 2 (which in some embodiments may not include the surface area 255) will determine the actual lifting pressure for a given main valve 220, but at this extreme of control system 310 operation the main valve 220 to open immediately after the pressure in the drive chamber 25 ilk the lifting pressure. Lifting pressure is applied with the piston 20 at the position in Figure 19 and critical pressure is applied with the piston at the position in Figure 20. With the control valve 215 closed or off during the entire stroke or closed at the moment the piston reaches the position in Figure 18, the drill operates at the highest possible frequency for the control system 310.
    Figures 21 and 22 illustrate one of the lowest frequencies at which the drill can operate the control system 310. In this operation, the control unit 125 hails the control valve 215 open until long after the lift pressure has been reached (ie after the piston 20 has risen past the point in Figure 19). ).
    The position of the piston 20, at which the control unit 125 disengages the control valve 215 in this operation is illustrated in Figure 21. The sensor 315 measures the position of the piston 20, the pressure chamber 25 or another parameter indicating to the control unit 125 that it is time to close the control valve 215.
    Since the pressure in the drive chamber 25 exceeds the lifting pressure, the main valve 2 opens immediately after the control signal has been switched off in Figure 21. Since the main valve 220 opens later in this, the drive chamber 25 reaches critical pressure later, as illustrated in Figure 22 (cf. Figure 20), that the drill operates at a lower frequency.
    The control unit 125 can be programmed or maneuvered manually in response to the sensor 3 scanning a selected value for a given parameter, such as the pressure of the drive chamber or the position of the piston. Frequencies between those in the two operating modes described above (Figures 19 and 20 in one mode and Figures 21 and 22 in another mode) can be obtained by changing the trigger point (which is a function of the parameter sensed by the sensor 315). at which the control unit 125 closes the control valve 215. In fact, the trigger point (and resulting frequency) is substantially spiritually adjustable below the control system 310. The control system 310 may be arranged to operate the drill at many different frequencies, not just the two discussed above with other embodiments. As a result, the frequency of drilling operation, instead of or in addition to the drill being diverted alternately in a sequence of first and second frequencies for conveying information to the surface, can itself convey messages (e.g. operation at a first frequency informs a receiver at the surface concerning a first type of information, informs operation at a second frequency receiver regarding a second type of information, etc.).
    Referring to Figure 23, the downward stroke, regardless of the control strategy used, is substantially the same. As the plug 100 is removed from the piston bore 90, the pressure in the drive chamber 25 drops as the drive fluid is blown out, and at the same time the main valve 220 closes if it was opened, due to the pressure drop in the drive chamber 25. The control unit 125 may even open the control valve 215 at this time. or earlier to assist in the closure of the main valve 220. The bottom 85 of the piston 20 moves away from the return shaft 70 so that the feed chamber 35 communicates with the return chamber 30 and drive fluid flows to the return chamber 30 to assist in the return stroke of the piston 20.
    Figure 24 is an alternative embodiment which schematically illustrates that the sensor means 120 is arranged within the piston 20. Figure is an alternative embodiment which schematically illustrates that the sensor means 120 is arranged between the drill bit 40 and the drill string 401. Figure 26 is an alternative embodiment which schematically illustrates that the sensor means 120 is arranged in the vicinity of the drill bit 40.
    Thus, the invention provides, inter alia, a submersible drill with variable frequency having the function of the frequency of the second drill during continuous operation of the drill. Various framing features and advantages of the invention are disclosed in the following claims. 16
    权利要求:
    Claims (23)
    [1]
    A sinker assembly (10) comprising: a supply of drive fluid (105) in the form of compressible fluid; and borrIcrona (40); a blowout structure (95) communicating through the drill bit (40) with the atmosphere; a reciprocating piston (20) with forward reciprocating motion with respect to the drill bit may be indicated by a drive chamber (25) disposed above the piston; a return chamber (30) disposed below the piston; means for driving the reciprocating motion of the piston by alternately connecting the drive chamber in connection with the supply of drive fluid and the return chamber in connection with the blow-out structure in a first instance, and placing the drive chamber in communication with the blow-out needle and the return chamber in contact with the feed in a second instance, a sensor (120) and a control unit (125) for generating a command signal, and means for changing, in response to the command signal and maneuvering via the control unit (125), the frequency with which the piston (20) delivers thrust load to the drill bit (40); wherein the sensor (120) and the means for changing the frequency are in operation when the drilling unit is down in the drill tail.
    [2]
    The submersible drilling rig of claim 1, wherein the means for changing the frequency includes means for changing the frequency during continuous operation of the drill.
    [3]
    The submersible drilling rig of claim 1, wherein the means for changing frequency comprises a chamber with an additional volume (135) and a valve (130) maneuverable via the control unit (125) between an open position, in which the valve (130) inserts the drive chamber (25). ) in connection with the chamber with an additional volume (135), and a closed state, in which the valve (130) switches off the connection between the chamber with an additional volume (135) and the drive chamber (25).
    [4]
    The sink drill assembly of claim 1, wherein the means for changing frequency comprises a chamber with an additional volume (135) and a valve (130), manoeuvrable via the control unit (125) between an open position, in which the valve (130) sanitizes the return chamber (30). ) in communication with the chamber with an additional volume (135), and a closed state, in which the valve (130) switches off the connection between the additional volume (135) chamber and the return chamber (30).
    [5]
    The sinker assembly of claim 1, wherein the means for changing frequency includes an actuator (140) operable via the timing change control unit (125) when the drive chamber (25) is connected to the blowout structure (95). 17
    [6]
    The sinker assembly of claim 1, wherein the means for changing frequency includes an actuator (140) manoeuvrable via the control unit (125) for changing the time when the drive chamber (25) is connected to the supply of drive fluid (105).
    [7]
    The sink drill assembly of claim 1, wherein the means of changing frequency includes an actuator (140) operable via the control unit (125) for changing the time when the return chamber (30) is salted in connection with the blowout structure (95).
    [8]
    The sinker assembly of claim 1, wherein the means for changing frequency includes an actuator (140) manoeuvrable via the control unit (125) for changing the time when the return chamber (30) senses in connection with the supply of driving fluid (105).
    [9]
    The submersible drilling rig of claim 1, further comprising a control system for sensing an operating parameter of the drill and maneuvering the means for changing frequency in response to the sensing of a predetermined operating parameter.
    [10]
    A submersible drilling rig according to claim 9, wherein the predetermined operating parameter is one of the position of the pressure and the piston.
    [11]
    The submersible drilling rig according to claim 10, wherein the sensor (120) is arranged in the drill bit (40) or between the drill bit (40) and the drill string (401).
    [12]
    A submersible drilling rig according to claim 10, wherein the sensor (120) is arranged in the vicinity of the drill bit (40).
    [13]
    The sinker assembly of claim 9, wherein the control system includes a control unit (125), a control valve (215) and a main valve (220); wherein the main valve (220) opens in response to a lifting pressure obtained in the drive chamber (25) to contact the drive chamber (25) in connection with the supply of drive fluid (105); and wherein the control unit (125) opens the control valve (215) to generate a control signal from the control valve (215) to the main valve (220) to delay the opening of the main valve after the lift pressure has been reached, for the second time before the opening of the main valve (220).
    [14]
    The sinker assembly of claim 1, wherein the means for driving the reciprocating motion of the piston includes a valve (130), and the means for changing the frequency comprises a mechanism for changing the time Mr operation of the valve (130).
    [15]
    The sink drill assembly of claim 14, wherein the mechanism for changing the timing of operation of the valve (130) is maneuverable during continuous operation of the drill.
    [16]
    The sinker assembly of claim 14, wherein the mechanism for changing the timing of operation of the valve includes a second valve (130) operable to open and close the connection between one of the drive (25) and return chambers (35) and a chamber having a additional volume (135).
    [17]
    The sinker assembly of claim 14, wherein the mechanism for changing the time Mr operation of the valve includes a mechanism for changing the time for connecting at least one of the drive chamber (25) and the return chamber (30) to at least one of the feed fluid drive (105). ) and the exhaust structure (95). 18
    [18]
    The submersible drilling rig of claim 14, wherein the mechanism for changing the time few operation of the valve includes a sensor (120) that monitors an operating parameter of the drill and generates the command signal in response to sensing a predetermined value of the operating parameter.
    [19]
    The sink drill assembly of claim 18, wherein the sensor (120) is disposed in the drill bit (40) or between the drill bit (40) and the drill string (401).
    [20]
    A submersible drilling rig according to claim 18, wherein the sensor (120) is arranged in the vicinity of the drill bit (40).
    [21]
    The sinker assembly of claim 14, wherein the mechanism for changing the timing of operation of the valve includes a control unit (125), control valve (215) and a main valve (220); wherein the main valve (220) opens in response to a lifting pressure obtained in the drive chamber (25) for communicating the drive chamber (25) with the supply of drive fluid (105); and wherein the control unit (125) opens the control valve (215) to generate a control signal from the control valve (215) to the main valve (220) to delay the opening of the main valve (220) after the lifting pressure is reached, for the second time of opening of the main valve (220). ).
    [22]
    A method of operating a sinker assembly at variable speeds, the method comprising: 1. driving the reciprocating motion of a piston (20) by alternately establishing and shutting off the connection between a feed fluid drive (105) in the form of compressible fluid and exhaust (95) and opposite spirits of the piston (80, 85) when the drill assembly is down in the drill tail; 2nd stroke of a drillIcrona (40) with the piston (20) once per operating cycle of the piston; and 3. during continuous operation of the drill, changing a time at which the connection between at least one of the opposite breaths of the piston and at least one of the supply of driving fluid (105) and the exhaust (95) is established and shut off.
    [23]
    The method of claim 22, wherein step (c) comprises sensing an operating parameter of the drill during continuous operation of the drill, which automatically generates a command signal in response to the operating parameter corresponding to a predetermined value, and, in response to the generation of the command signal, maneuvering a mechanism for changing the timing of the connection between at least one of the opposite spirits of the piston and at least one of the supply of propellant fluid and the exhaust. 19
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    の密ののみクご1997|ykkS RASTER
    同族专利:
    公开号 | 公开日
    US8215419B2|2012-07-10|
    SE1151155A1|2011-12-05|
    WO2010129675A3|2011-01-06|
    WO2010129675A2|2010-11-11|
    US20100282509A1|2010-11-11|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    US12/436,261|US8215419B2|2009-05-06|2009-05-06|Variable frequency control for down hole drill and method|
    PCT/US2010/033733|WO2010129675A2|2009-05-06|2010-05-05|A down hole drill assembly and a method of operating a down hole drill assembly|
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