MXPA00011901A - A device and method for regulating fluid flow in a well - Google Patents

Abstract

A device for mutually independent control of regulating devices (1-6) for controlling fluid flow between a hydrocarbon reservoir (50) and a well (51) comprises a flow controller (54) and a hydraulic actuator (56). The actuator (56) is flow-relatedly arranged in series with at least two associated control valves (20-25) in a path (18, 19) between two hydraulic pipes (11, 14). The control valves (20, 25) are controlled to open for the flow of hydraulic liquid to the actuator (56) by the pressure in the two hydraulic pipes (11, 14), and the combination of two hydraulic pipes (11, 14) which are connected to an actuator (56) is different for independently controllable regulating devices (1-6).

Description

DEVICE AND METHOD FOR REGULATING FLUID OF FLUID IN A WELL DESCRIPTION OF THE INVENTION A device for the reciprocally independent control of regulation devices to control fluid flow between a hydrocarbon reservoir and a well that extends from an initial area to the reservoir of hydrocarbon. wherein the regulating devices are provided in the well in the hydrocarbon reservoir, where each regulating device comprises a flow controller with a regulating element that can be moved between the regulating positions for the fluid flow and is connected To an actuator element of a hydraulic actuator, the hydraulic actuator is provided with two hydraulic ports, the actuator element can be moved between the regulation positions with a minimum pressure differential between the ports, the differential pressure is provided by the hydraulic pipes that they extend from the well start area to the hydrocarbon reservoir. In the recovery of hydrocarbons from hydrocarbon reservoir wells are drilled from a start area, which may be the - * - * • - * ~? C seabed or the surface of the Earth, down in the reservoir. Wells are lined with coatings to prevent the well from collapsing. The liner is drilled in the reservoir area, thereby allowing the hydrocarbons to flow into the well. Inside the liner a pipe is placed to drive the hydrocarbon flow to the start area. The hydrocarbon deposits are located in isolated cavities, which can have a large horizontal area. In the case of such deposits, the well is drilled vertically below the surface, whereby the well is directed horizontally into the reservoir. The flow of hydrocarbons within the retreat causes the pressure to become higher towards the end of the well. This pressure differential is undesirable, since it can result in the penetration of water and gas into areas with low pressure, which can result in flow problems and reduced well production. In order to control the inflow into the well along the length of the well, and to allow the well to close in some areas, displacement or rotation sleeves are employed with --- * • -'- * - flow openings that can be closed by a regulating element that is pushed in the longitudinal direction of the well or rotated about the longitudinal axis of the well. The sleeves are an integral part of the r e s t imi e n t / t ub e r a. They move by electric or hydraulic motors, and are operated from the start area of the well by means of electric cables and / or spiral pipe with hydrostatic pressure. The sleeves must be able to be controlled both to an open and closed position, and therefore, when using direct hydraulic control, there must be two spiral pipes for each sleeve. The number of sleeves can be large, 10 or more, and the direct hydraulic control of each sleeve can therefore involve a large number of spiral tubes. So the normal procedure is to use a system where the energy to move the regulating elements of the sleeves is supplied hydraulically, and the control of the hydraulics is performed electromechanical valves. The well can have a depth of 2000 meters, and a horizontal length of 3000 meters, with the result that the length of the transfer cables and spiral tubes is formidable. Because of installation costs and operational problems, it is therefore desired to restrict the number of spiral cables and tubes. The low pressure in the well can be from 200 to 300 bar, while the temperature can be between 90 and 180 ° C. In these environmental regulating devices, and particularly electromechanical components, they frequently become defective after a short term of use. The economic consequences of not being able to control the inflow into the well are enormous, and consequently it is desired to find devices to control the flow of hydrocarbons that are simpler and more reliable than the current devices, and particularly it is desired to avoid the electromechanical components in the deposit area. When water or gas is injected into the hydrocarbon reservoir, water or gas in some places can flow directly into a production well, and consequently in the case of injection wells it is also desired that they are able to control or close the flow from the well to the deposit in specific areas.

US-A-4 945 995 discloses a method and a device for the reciprocally independent hydraulic control of at least two devices, including flow regulation devices provided in production zones in a well. An object of the method and the device is to reduce the number of hydraulic interconnecting piping required for control. This is achieved with a combined electro-hydraulic solution. O-98/09055 describes a method and device for the selective control of devices arranged below in a well. The control comprises electrical and hydraulic signal connections. The object of the invention is to provide a device and a method for the reciprocally independent control of regulation devices for controlling fluid flow between a hydrocarbon reservoir and a well extending from a starting area to the hydrocarbon reservoir, whose device and The method will be simpler than known devices and methods, and where the components used in the deposit area will be solid and reliable. A further object is that the number of spiral tubes and / or cables will be less than in the case of known devices and methods. Additional objects will be apparent from the special part of the description. The objects are achieved according to the invention with a device and method of the type mentioned in the introduction which are characterized by the features set out in the claims. In the invention the energy and control signals are transferred to the regulating devices only by means of hydraulic tubes. Electrical cables and electromechanical components are avoided in their entirety, resulting in simpler, more robust and more reliable control of fluid flow. Compared to the number of tubes in s p i r a 1 / cables that are used in the prior art, with the invention some hydraulic tubes can be used for the independent control of the same number of regulating devices, thereby simplifying the control. This will be further explained in the special part of the description. The invention will now be explained in more detail together with a description of a specific embodiment and with reference to the drawings in which: Figure 1 illustrates a well for the recovery of hydrocarbons in the continental shelf. Figure 2 illustrates a rotation sleeve for controlling inflow in the well. Figure 3 illustrates a cross section through a pipe that is employed in the invention, taken along the line of intersection III-III in Figure 1. Figure 4 illustrates the connection between the hydraulic pipes and the hydraulic devices. regulation that are employed in the invention. Figures 5-9 illustrate different arrangements of the hydraulic control valves that may be employed in the invention. Figure 10 illustrates a preferred hydraulic control valve according to the invention. Figure 11 illustrates a longitudinal section through a regulating device according to the invention. Figures 12-13 illustrate cross sections through the regulating device, taken along the intersecting line XII-XII in Figure 11, together with the hydraulic tubes and control valves. Figure 1 illustrates a well 51 for the recovery of hydrocarbons in the continental shelf. The well 51 is drilled from the seabed 59 to a substantially horizontal hydrocarbon reservoir 50. In a start area on the seabed, the well is connected to a wellhead 52 and an ascending tube 63 to a floating platform 53 located at sea 62. Well 50 is lined with a skin 69, and the well a pipe 64 is inserted to transport hydrocarbons from the tank 50. As mentioned in the general part of the description, the tank can be located 2,000 meters under the seabed, and the horizontal hydrocarbon production part of the well can have a length of 3,000 meters. The well produces different amounts of hydrocarbons in different production areas, only two of which are illustrated with reference numbers 60 and 61. In order to control production, regulation devices can be introduced into production areas.

Figure 2 illustrates a regulating device 1 that is inserted into the trough 64 in a production zone to control inflow into the well. The regulating device comprises a flow controller 54 in the form of a rotation sleeve 67 with flow openings 68 and an internal adjustment element that is not illustrated in Figure 2. The adjustment device 1 also comprises an actuator 56 accommodated in the housing 76 of the actuator for driving the flow controller 54. In addition, the regulating device comprises control valves not shown for controlling the flow of the hydraulic fluid for the actuator 56. Figure 2 should be understood in general terms, and applied to the prior art and to the invention. Figure 3 illustrates a cross-section through a pipe which is employed in the invention, taken along the line of intersection III-III in Figure 1. The hydraulic pipes, numbered herein with four hydraulic pipes 11 -14, are accommodated on the outer side of the pipe 64, within the jacket 17. The hydraulic pipes 11-14 extend from the well start area, ie the well head 52, to the tank. The start area can also be a ground wellhead, or the hydraulic pipes can be driven to a platform or a production vessel. Figure 4 illustrates the connection between the hydraulic pipes 11-14 and the regulation devices 1-7 used in the invention. the regulating devices are illustrated schematically, and as mentioned with reference to Figure 2 each regulating device comprises a flow regulator, an actuator for the flow controller, and control valves for controlling the flow of hydraulic fluid between the hydraulic pipes and the actuator. the hydraulic pipes are connected in two for each regulation device. It can be seen that the combination of two hydraulic tubes that are connected to the regulating devices is different to regulate the devices 1-6, and the regulating device 7 is connected to the same hydraulic tubes as the regulating device 5, i.e. hydraulic tubes 11 and 13. Figures 5-9 illustrate the different arrangements of the hydraulic control valves that may be employed in the invention. The invention is not limited to a specific number of hydraulic tubes, a specific number of regulating devices or a specific arrangement of control valves, and for easy understanding of the presentation, only those control valves for device 1 are mentioned. regulation, which are connected to hydraulic pipes 11 and 14. Figure 5 illustrates the four hydraulic pipes 11-14, a hydraulic actuator 56 and the two control valves 20 and 21, which are located in a hydraulic path 18, 19 between the hydraulic pipes and the actuator. The actuator is illustrated schematically, and comprises a static portion 70, and a movable actuator element 57, which are in the form of segments of a circle, and are accommodated in an annular space that is externally bounded by an actuator housing circular not shown and is internally limited by a circular inner wall not shown forming an extension of the wall of the pipe. The static portion 70 and the actuator element 77 define a first and second hydraulic chamber 71 and 72 respectively with hydraulic ports 15 and 16 respectively. The control valves 20 and 21 control the flow of the hydraulic fluid between the actuator 56 and the hydraulic pipes and are the hydraulic control valves of the type that open and close for the flow of the hydraulic fluid in the presence and absence respectively of at least one opening pressure on a control port 30 and 31 respectively. The illustrated control valves are of the pressure controlled control valve type with a return spring that in the absence of pressure in the control port moves the valve to the closed position, and they are illustrated schematically according to the standardized rules. With reference to the valve 21, the upper square 65 illustrates a path interrupted through the valve, showing the valve in the closed position. The lower square 66 illustrates a path that opens in both directions, showing the valve in the open position. The reference number 41 illustrates the return spring, ie a spring that moves the valve to its neutral position, which for these valves means the closed position, in the absence or presence in the control port 31. In accordance with the standardized rules, the valve 21 is shown connected in the path 18 in its neutral position. When at least one open portion is applied to the control port 31, the spring 41 is compressed, and the valve is moved to the open position. In Figure 5-9, the valves, control ports, and return springs are indicated by reference numbers 20-25, 30.35 and 40-45 respectively, with the last identical figure for the same valve. According to the invention, the actuator 56 is accommodated in related flow by ports 15, 16 in series with at least two associated control valves in the hydraulic path between two hydraulic tubes. Figure 5 illustrates the actuator 56 accommodated in flow related in series with the control valves 20, 21 between two hydraulic tubes 11, 14, thus illustrating at least the number of control valves that are needed according to the invention. According to the invention, the control port on at least one of the control valves will be connected to one of the hydraulic pipes, and the control port on at least one of the other control valves will be connected to the other pipe. hydraulic. In Figure 5, the control port 30 on the control valve 20 is connected to the hydraulic pipe 11 by the hydraulic path 18, and the control port 31 on the control valve 21 is connected to the hydraulic pipe 14 by the path 19 hydraulic that is in accordance with the invention. When the regulating device is controlled, the two hydraulic tubes that are connected to the control valves by the actuator of the regulating device are pressurized with hydraulic fluid to at least the opening pressure of the associated control valves. This is done by pumping hydraulic fluid under the hydraulic pipes from the well's start area. With reference to Figure 5, the regulating device 1 is controlled by pressurizing the hydraulic tubes 11 and 14 to a pressure that is greater than the opening pressure for the control valves 20 and 21, typically 75 bar. The control valves 20 and 21 consequently open for the flow of hydraulic fluid in the paths 18 and 19, between the hydraulic tubes 11 and 14 and the actuator 56. The first and second hydraulic chambers 71 and 72 respectively in the actuator 56 are consequently connected to the hydraulic tubes 11 and 14 respectively. The pressure is then increased in one of the hydraulic tubes 11 or 14, thus establishing a pressure differential between the ports 15, 16, for example, between the first and second hydraulic chambers. When the pressure differential is large enough to overcome the internal friction in the regulating device 1, the actuator element 57 moves. The pressure in the hydraulic tube that has the much larger pressure can be 200 bar, while the pressure in the hydraulic tube that has the much lower pressure can be in the opening pressure for the control valves or slightly higher. It will be noted that the actuator element 57 moves in the direction Ri when there is an overpressure in the first chamber 71, and in the direction R2 when there is an overpressure in the second chamber 72. The actuator element 57 is connected to the regulating element in the controller. flow, with the result that the settling of the pressure difference between the hydraulic tubes causes a performance of the flow controller in a direction that depends on the direction of the pressure differential. Figure 6 illustrates a valve arrangement where the control valve 20 or 23 is accommodated in related flow on each side of the actuator 56. When the hydraulic pipes are pressurized, this valve arrangement will operate in the same manner as the valve arrangement that it is illustrated in Figure 5. The valve arrangement in Figure 6, however, may have operational advantages, such as gas bubbles or impurities, for example, which may be present in the hydraulic pipe 14 when it is not pressurized, are stopped by the valve 23, thus preventing them from moving in the actuator 56. Figure 7 illustrates an arrangement of the control valves corresponding to Figure 6, with the difference that the control ports are connected in opposite hydraulic tubes. Compared to the valve arrangement in Figure 6, this valve arrangement has the advantage that none of the chambers in the actuator 56 will be pressurized if only one of the hydraulic pipes is pressurized.

Under the ideal hydraulic operating conditions, fully controlled and incompressible compression, the gas-free hydraulic fluid, the valve arrangements in Figures 5-7, will offer complete control of the regulation device 1. However, in practice, the hydraulic pressures in the hydraulic tubes will vary with time, and the gas may appear in the pipes, resulting in a compressible hydraulic medium and difficulties in fully controlling the pressure. Only by pressurizing one of the hydraulic tubes to a pressure that is greater than the opening pressure of the control valves, unwanted movements may arise with these valve arrangements of the actuating element. Figure 8 illustrates a valve arrangement where each side of the actuator 56 is accommodated in related flow, the two control valves 20, 21 and 22, respectively, and where the two control valves are located on the same side of the actuator it has control ports, which are connected to a different hydraulic pipe, illustrating that the control ports 30 and 33 are connected to a hydraulic pipe 11, while the control ports 31 and 32 are connected to the hydraulic pipe 14, in this case valve arrangement both chambers 71 and 72 are cut off from the connection with the hydraulic pipes until the hydraulic pipes 11 and 14 are pressurized to a pressure that is higher than the opening pressure of the pressure valves, thereby avoiding the problem above-mentioned potential with the valve arrangements illustrated in Figures 5-7. Figure 9 illustrates a valve arrangement where the two control valves, which are located in related flow on each side of the actuator and which have control ports that are connected to the same hydraulic pipe, are composed of a valve unit 24 or 25 control with a port 34 and 35 of common control respectively. From a functional point of view, the valve arrangement in Figure 9 is identical with the valve arrangement of Figure 8, since valve 24 can be understood as a combination of valves 21 and 22 and valve 25 can be understood as a combination of valves 20 and 23. With reference to Figure 4 it can be seen that when the hydraulic pipes 11 and 14 are pressurized to a pressure that is greater than the opening pressure of the control valves, one of the hydraulic pipes is pressurized simultaneously in regulation devices 2, 3, 5 and 7. With a valve arrangement as illustrated in Figures 5 or 6, to regulate the devices 2 and 3, which are connected to the hydraulic tube 14, this will result in the pressurization of the second chamber 72. The trajectory 18 of the first chamber 71, however, is closed, and under ideal operating conditions, as mentioned above, the pr esurization of the second chamber 72 will not result in any movement of the actuating element 57. However, as mentioned above, gas bubbles may occur or other factors may arise that cause movement in the actuator element. It may be obvious that this problem is less serious with a valve arrangement as illustrated in Figure 7, and is virtually eliminated with a valve arrangement as illustrated in Figures 8 and 9. Figure 10 illustrates one embodiment of the valve corresponding to the valve arrangement that is illustrated schematically in Figure 9, with the difference that the paths 18, 19 in Figure 9 go in the same direction, while those in Figure 10 go in the opposite direction, that does not matter for the function of the valves. The only reference numbers in Figure 10 that are not shown in Figure 9 are 94 and 95, which indicate a division in valves 24 and 25 respectively. The valves 24, 25 are of a standard type, and therefore a description of their function will be omitted. It can be seen that the valves 24, 25 are assembled together in an oblong unit. Figure 11 illustrates a longitudinal section through a regulating device according to the invention, in the form of a rotation sleeve 67, which is inserted into the pipe 64. The hydraulic pipes are not shown. The valves 24 and 25 are designed as illustrated in Figure 10, and are accommodated within the wall of the housing 76 of the actuator. Also shown are the actuator 56 with the actuator element 57, and the flow controller 54 with the flow openings 68 and the regulating element 55. The actuator element 57 is securely connected to the regulating element 55, thereby effecting a direct rotation thereof by means of rotation in the actuator 56 as a result of an applied hydraulic pressure differential.

The hydraulic trajectories 18 and 19 are not illustrated in Figure 11. They are in the form of channels or passages in the housing of the actuator and other construction components that are part of the regulation device, and which will not be described in detail. Figure 12 illustrates a cross-section through the actuator 56, taken along the line of intersection XII-XII in Figure 11, together with a schematic illustration of the associated hydraulic paths and control valves. Reference should be made to Figures 5-10 for a general understanding of Figure 12. From the cross section through the actuator 56 it can be seen that the actuator 57 and the static portion 70 define the first and second chambers 71 and 72 respectively . When there is a pressure differential between ports 15 and 16, the actuator element is rotated depending on the direction of the pressure differential. It can be seen that the actuator element 57 is provided with a chamber 85 of the inner deflection tube that is serrated in end areas by check valves 86, 87, which only allow flow within the interior deflection tube chamber 85. In addition, the actuator element 57 has an outer deflection tube chamber 74 which is connected to the interior deflection tube chamber 85 through a deflection tube channel 75. Prior to a more closed description of Figure 12, reference may be made to Figure 13, which illustrates the actuator 56 after the actuator element 57 is moved in the direction R3 to an extreme position as a result of a pressure differential applied between the ports 15 and 16, the pressure is much higher in the port 16. It can be seen that in its extreme position, the actuator element 57 closes the passage between the first chamber 71 and port 15, since at the same time a passage between the outer deflection tube chamber 74 and the port 15. A thorough passage is consequently opened from the second chamber 72, through the verification valve 86, the interior deviation tube chamber 85, the channel 75 of deflection tube, the outer deflection tube chamber 74, to port 15, and since the hydraulic fluid is located in the second chamber 72 it has a higher pressure than in port 15, the hydraulic fluid f It will go through the exhaustive passage. By means of an appropriate dimension of the exhaust passage and the hydraulic system, this production will result in a pressure drop of the hydraulic fluid and / or an increase in the flow rate of the hydraulic fluid. By checking the pressure in the two hydraulic tubes 11, 14 and the action during the flow rate of the hydraulic fluid, it is possible to detect when the actuator element 57 and the regulating element 55 have reached the extreme position. By the application of overpressure to port 15 in relation to port 16, the production of the hydraulic liquid will stop, and the check valve 86 will close. It can be seen from Figure 13, that an overpressure at port 15 will not be able to move the actuator element 57, and an end port 15 'which is connected to port 15, is accommodated by the both in close proximity to the portion 70 static. The pressure is thereby transmitted to the port 15 'and the hydraulic fluid is pressed against the end of the actuator element 57, thereby causing it to move in the opposite direction R3. By means of the movement of the actuating element away from the position e trema, the connection is broken between the port 15 and the chamber 74 of external deflection tube, thus closing the exhaust passage. The extreme position of the actuating element is one of several possible adjustment positions, and it should be understood that they correspond to exhaustive passages that can be provided by other adjustment positions. The internal hydraulic volume of the actuator, that is, the total volume of the first and second chambers 71 and 72 respectively, it will be a known size. Check the pressure in the two hydraulic pipes 11, 14 and the volume of production of the hydraulic fluid between the hydraulic pipes 11, 14 during the operation, which can be imp ened by a pressure measurement and a volumetric measurement in the starting area This allows a calculation of the actuator element 57 and thus the adjustment position of the regulating element 55 after a lapse of time. The action starts when the pressure in the hydraulic tubes exceeds the opening pressure of the control valves, and the production volume of the hydraulic fluid during the actuation must therefore be measured from this point in time. In contrast to the embodiments illustrated in Figures 5-10, in the embodiment illustrated in Figure 12, between the actuator 56 and each of the hydraulic tubes 11, 14, a self-contained trolley metering valve 77 is accommodated. in flow related in series with each control valve 24, 25. The dosing valve 77 is of the type in which an internal volume 79 is filled. with affluent liquid by pressurization of the entrance 78, so that the influx stops until the entrance 78 is depressurized. By means of the repeated presorption of the inlet 78, the dosing valve 77 deliberates the liquid of the internal volume 79 which is achieved as follows: When there is an overpressure at the inlet 78, the hydraulic fluid flows into the internal volume 79, causing that a piston 80 compresses a return spring 81. A diverter tube valve 83 is provided in a diverter tube 84 and controlled by the same pressure inducing the inlet 78. The diversion tube valve 83 is of the pressure-controlled directional control valve type with return spring, that in the absence of pressure in the control port moves the valve to the open position, the diverter tube valve 83 consequently closes the diverter tube 84 when the inlet 78 is budgeted. When the piston 80 is pushed towards the bottom of the dosing valve 77, the inflow of the hydraulic fluid stops. At this point, the pressure at the inlet 78 is released, which can be carried out manually or automatically from the bed's start area, whose squeezing causes the diverter tube valve 83 to open for the flow of the hydraulic fluid from the reservoir. internal volume 79 above the piston, through the diverter tube 84, to the internal volume 79 below the piston. The return spring 81 pushes the piston 80 upwards, resulting in this hydraulic fluid flow. At the same time a check valve 82 prevents the hydraulic fluid from flowing into the metering valve from the downstream side. By means of the repeated urging of the inlet 78, the new hydraulic fluid fills the internal volume 79, and the hydraulic fluid which is located in the internal volume 79 below the piston is forced out of the valve 77 of dosage.

Counting the number of pr esurizaci on is repeated from the entry 78, based on the knowledge that is related to the internal volume 79 it is possible to calculate the volume of production of the hydraulic fluid with greater accuracy than by a volumetric measurement in the starting area of the ground, thus achieving a more accurate determination of the actuator element 57 and with this the regulating position of the regulating element 55. For a further description of the invention, reference is again made to Figure 4. As mentioned, the combination of two hydraulic tubes that are connected to a regulation device is different for the regulation devices 1-6. By pressurizing the hydraulic tubes 11 and 14, an independent control of the regulating device 1 is obtained. Similarly, by pressurizing the selected combinations of the hydraulic tubes, a control reciprocally independent of any of the regulation devices 1-6 can be obtained. The regulating device 7 is connected to the same hydraulic tubes as the regulating device 5, these two regulating devices have this common control and form a regulating device group. When there is a large number of regulating devices, it is thus possible to group the regulating devices into groups of reciprocally independent regulating devices. It is also possible to perform a more complex control by pressurizing several hydraulic pipes simultaneously, with the possibility of different pressure levels, with the result that the hydraulic pipe that is pressurized at the highest pressure for a regulation device represents the lowest pressure for another regulation device. Figure 4 shows how 4 hydraulic tubes offer the possibility of independent control of a maximum of 6 regulation devices. It is further illustrated that with 3 hydraulic tubes it is possible to control 3 independent regulation devices. Similarly, 5 hydraulic tubes offer the possibility of 10 independent regulation devices, 6 hydraulic tubes correspond to 15 independent regulation devices and so on. If the number of hydraulic pipes is designated in n and the maximum number of independent regulation devices is designated in N, it will be observed that N increases by nl, when n increases by 1. It will also be observed that n = 2 is the lowest possible value For n, and in this case N is 1. So for n, the hydraulic N tubes is the total of a geometric series where the first term is 1, the highest term is nl and the number of terms nl. From mathematical theory it is known that the total of a geometric series is the total of the first and the last term multiplied by the number in the series, divided by 2. Therefore this results in N = [(1 + nl) (nl )] / 2 = n (nl) / 2. When a number of regulating device is independently controlled according to the prior art, in the case of direct internal control, two hydraulic tubes must be used for each regulating device. In the case of electromechanical control, the number of hydraulic tubes can be limited to two, since two electrical cables can be used for each regulation device. With the regulation devices N, at least 2 N cables or spiral tubes can therefore be used. In addition, it is desired to receive r e t r o 1 a t ion from the reservoir concerned when the regulating elements have assumed the specific regulation positions, which can be implemented with limit switches that result in an additional increase in the number of cables. It is possible, of course, to transfer signals with sophisticated electronic elements, thus reducing the number of electric cables, although this requires the use of electronic equipment in the deposit area that has been shown to be untrustworthy because of the pressure and particularly the temperature in the tank. With the invention, the number of hydraulic tubes therefore necessary for the independent control of a given number of regulating device is less than the number of tubes in p 1 r to 1 / c to 1 e required in the prior art. From the formula N it is observed that this advantage of the invention is relatively much greater for a large number of hydraulic tubes than for a small number. To achieve any substantial advantage with the invention, the number of hydraulic tubes must be at least three. From the above it should be obvious that the invention will also function to control the flow of fluid from a well to a reservoir. The invention can therefore also be used when water or gas is injected into a reservoir.

Claims (10)

1. CLAIMS 1. Device for the reciprocally independent control of regulation devices to control fluid flow between a hydrocarbon reservoir and a well that extends from a start area to the hydrocarbon reservoir where the regulation devices are roporcionado in the well in the hydrocarbon reservoir, where each regulating device comprises a flow controller with a regulating element that can be moved between the regulation positions for the fluid flow and is connected to an actuator element of a hydraulic actuator, the hydraulic actuator is Equipped with two hydraulic ports, the actuator element can be moved between the regulation positions with a minimum pressure differential between the ports, the differential pressure is provided by the hydraulic tubes that extend from the well start area to the hydrocarbon reservoir , characterized in that each regulation device purchased At least two control valves to control the flow of the hydraulic fluid between the actuator ports and the hydraulic tubes, the control valves are of the type that opens and closes for the flow of the hydraulic fluid and the presence and absence respectively of at least one opening pressure in a control port, where the actuator is accommodated in related flow through the ports in series with the control valves in a hydraulic path between two hydraulic tubes, and the control port in at least one of the control valves that is connected to one of the hydraulic pipes, and the control port on at least one of the other control valves that is connected to the other hydraulic pipe, and the combination of two hydraulic pipes that are connected to an actuator is different for independently controllable control devices.
2. 2. Device according to claim 1, characterized in that it is accommodated in related flow in at least one of the control valves on each side of each actuator.
3. 3. Device according to claim 1 or 2, characterized in that two of the control valves on each side of each actuator are accommodated in related flow, and the two control valves have control ports each of which is connected to the tube respective hydraulic.
4. 4. Device according to claim 3, characterized in that the two control valves that are located in related flow on each side of the actuator, and that have control ports that are connected to the same hydraulic pipe are composed of a control valve unit with a common control port.
5. 5. Device according to any of the preceding claims, characterized in that the actuator is provided with at least one exhaust passage that is open for the production of hydraulic fluid when the actuator element is located in regulation positions, and which is closed when the actuator is closed. Actuator element is located on the outer side of the regulation positions.
6. 6. Device according to any of the preceding claims, characterized in that between each actuator and each of the hydraulic tubes to which the actuator is connected, a self-contained metering valve, in series with the valve, is accommodated in a related flow. of control and the dosing valve is of the type in which an internal volume is filled with affluent liquid in pressurization of an inlet that is depressurized, and that by means of the repeated pressurization of the inlet the liquid of the internal volume deliberates.
7. 7. Method for the reciprocally independent control of regulation devices for controlling fluid flow between a hydrocarbon reservoir and a well extending from a starting area to the hydrocarbon reservoir and by a device according to the preceding claims, characterized in that the two hydraulic tubes that are connected to the two control valves for regulating the actuator of the device are pressurized with hydraulic fluid to at least the opening pressure of the associated control valves, whereby the valves of associated controls open for the flow of hydraulic fluid between the two hydraulic tubes and the actuator and that between the two hydraulic tubes a pressure differential is set that is large enough to move the actuator element, whereby the actuator drives the controller flow.
8. 8. Method according to claim 7, when using a device according to claim 5, characterized in that the pressure in the two hydraulic tubes and the flow rate of the hydraulic fluid are checked during the actuation and since the exhaustive passages are open when the actuator element is located in the regulating positions, the regulating positions of the actuating element and the regulating element are detected as a pressure in the hydraulic fluid and / or an increase in the hydraulic fluid flow rate.
9. 9. Method according to the claim 7, characterized in that the pressure in the two hydraulic pipes and the volume of production of the hydraulic fluid between the two hydraulic pipes are checked during the actuation, and the regulating positions of the actuating element and the regulating element are calculated based on the volume internal hydraulic and the production volume of the hydraulic fluid actuator during the performance.
10. 10. Method according to claim 7, when a device according to claim 6 is used, characterized in that the volume of production of the hydraulic fluid is calculated based on the internal volume of the dosing valve and the number of pressurization the entrance .