Abstract:
To investigate the quality and nature of perforations in a downhole environment, a ‘pecking’ finger and depth measuring probe that can be axially and radially displaced enables the perforation to be located and its depth determined, through sequentially pecking around the wall lining. By swinging a pecking finger supporting a depth measuring probe tip and measuring the displacement of the finger, the edge and center of the hole can be determined with the largest displacement being when the tip is fully in the hole. The depth measuring probe is then deployed and the depth of the perforation established by an increase in the force required to push the probe and by the displacement of the pecking finger as it is pushed back by the reaction forces. Radially extendable clamps at the ends of the tool fix the tool with a surrounding bore.

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
     The present application is a 371 National Stage Application of and claims priority of International patent application Serial No. PCT/GB2009/001108, filed May 1, 2009, and published in English the content of which is hereby incorporated by reference in its entirety. 
     FIELD OF THE INVENTION 
     The present invention relates to a downhole tool. 
     BACKGROUND ART 
     In the field of oil and gas exploration, it is usual to drill the well by first drilling the necessary hole, lining this with a steel liner, and backfilling behind the casing with cement. Prior to cementing the casing, drilling takes place under a fluid column of drilling mud. The hydrostatic pressure of the mud prevents flow of fluids from the downhole oil reservoir and/or aquifers into the well. Once the casing is cemented into place, the drilling mud is replaced by a lower density fluid, so that the hydrostatic pressure is less then the natural reservoir pressure. The casing can then be perforated adjacent to the oil producing zone, to allow the oil to flow into the well and to surface. 
     A perforating gun is used to perforate the well casing. The perforating gun is lowered down the oil well by a wire line to a predefined depth. It contains within it a series of explosive charges which, when detonated, fire projectiles or jets through the lining wail, thus creating orifices (perforations) through which the oil or gas can flow into the wellbore. Typically, a successful perforation will be of the order of 500 mm deep and 5 mm in diameter. Several perforations may be made, at a typical density of between 4 and 10 perforations per 300 mm. 
     From time to time, an attempt to create perforations is unsuccessful, in that it results in no flow or an inadequate flow. At present, there is no feasible way of investigating the quality of the perforations, so in such circumstances it will not be clear whether the poor flow is attributable to unsuccessful perforation (such as failure of the shaped charges) or to some external factor such as a lower than expected permeability of the rock around the hole. 
     SUMMARY OF THE INVENTION 
     Problems can therefore occur, typically with debris blocking these orifices which affects the well output. Where there is low yield from the well, this could be due either to the underlying nature of the oil reservoir, or due to problems with the perforations. There is a need therefore to be able to verify the quality of the perforations, principally to determine the orifice depth for a pre-defined minimum diameter. 
     The present invention seeks to provide a means of investigating the quality and/or nature of perforations in a downhole environment. Embodiments of the invention described in this patent application provide a tool that can assist in locating perforations and checking the perforation depth. Additionally, as the tool includes a mechanical probe to determine the perforation depth, it may also be possible to use it as a means to dislodge debris where present. The mechanical probe may also include a sensor, for measuring other parameters of the perforation hole, such as the surrounding rock resistivity, that can determine to what depth drilling mud filtrate has invaded the reservoir rock. 
     The invention therefore seeks to produce a tool which can be lowered to within close proximity of the well casing perforations that can be rigidly fixed and centralised to the well casing, and which has a ‘pecking’ finger and depth measuring probe that can be axially and radially displaced enabling the perforation to be located and its depth determined. There are well established techniques for positioning a down-hole tool to within a few inches of its intended location relative to the producing formation. 
     Having thus positioned the tool and locked it to the wall casing, embodiments of the invention allow the exact position of a perforation to be determined by techniques that include sequentially pecking around the wall lining in patterns such as radial, axial, and spiral sequences. By swinging a pecking finger that supports a depth measuring probe or cable with a bullet or conically shaped tip and measuring the displacement of the finger, the edge and centre of the hole can be determined with the largest displacement being when the tip is fully in the hole. When this position has been determined, the depth measuring cable is deployed and the depth of the perforation can be established by both an increase in the force required to push the cable and by the displacement of the pecking finger as it is pushed back by the reaction forces on the cable. Further details of the manner by which this can be achieved in preferred versions of the invention are described below. 
     Thus, in its first aspect the present inventions provides a downhole tool comprising a elongate housing for insertion into a downhole environment, from which a probe extends radially by a variable amount, means for driving the probe in a radial direction, and means for sensing resistance to outward radial movement of the probe. 
     The probe is preferably stored axially in the housing so that a sufficient length can be accommodated without the housing without needing to adopt excessive dimensions. It should be sized to fit within a perforation, and is preferably flexible so as to allow it to bend between a longitudinal and a radial disposition. It can extend from an axially rotateable part of the tool, such as a central section of the housing. 
     The probe is preferably moveable axially along the tool. To this end, it can be supported on a probe carriage that is moveable longitudinally within the housing such as by means of a lead screw. The probe can then extend through a probe guide shaped to bend the probe from a longitudinal direction within the housing to a radial direction external to the housing, also moveable longitudinally within the housing such as by means of a lead screw. 
     Resistance to further radial movement of the probe can be detected by applying a radially outward bias relative to the housing to the probe guide, and including a means for sensing movement of the guide against that bias. When the probe is unable to move radially further, an attempt to make it do so will cause the probe guide to recoil inwardly. Alternatively, or in addition, the torque applied by the motor driving the probe can be detected. 
     The probe can be made rotateable about the radial axis along which it extends, to assist in guiding it into a perforation and in clearing that perforation. Alternatively, or in addition, the probe can be made to proceed into the perforation in a reciprocating manner. In the latter case, the probe might withdraw slightly on reaching an obstruction before recommencing forward movement. This could be combined with a small rotational adjustment of the tool, and would assist in easing the probe into the full depth of a potentially irregular perforation. 
     One or more radially extendable clamps can be provided for fixing the tool within a surrounding bore. These can be at the upper and/or lower ends of the tool. Ideally, they are moveable between an extended and a retracted position by interengagement with a member moveable relative to a remainder of the tool in a direction that is longitudinal relative to the tool. The member can be, for example, a sleeve extending longitudinally around the tool, the sleeve being moveable longitudinally along the tool. 
     In a further aspect, the present invention relates to methods of investigating a downhole bore. A first method comprises the steps of providing a tool as defined above, locating the tool within the bore, driving the probe in a helical manner, whilst doing so, periodically extending the probe thereby to locate perforations in a wall of the bore. After locating a perforation, the probe can be extended into the perforation to ascertain the depth thereof. A second method allows for the detection of perforation sites via an alternative sensing method such as a suitable electrical sensor adapted to detect metal or the absence thereof. Once a perforation is detected, the probe of a tool as defined above is then extended into the perforation as before. 
     The clamps referred to above could be used to fix other types of tool in place in a downhole environment or one similar. Accordingly, in a still further aspect the present invention provides a downhole tool comprising an elongate housing for insertion into a downhole environment, at least one radially extendable clamp for fixing the tool within a surrounding bore, moveable between an extended and a retracted position by interengagement with a member moveable relative to a remainder of the tool in a direction that is longitudinal relative to the tool. As before, the member can be a sleeve extending longitudinally around the tool, the sleeve being moveable longitudinally along the tool and such clamps can be provided at an upper and/or a lower end of the tool. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       An embodiment of the present invention will now be described by way of example, with reference to the accompanying figures in which; 
         FIG. 1  shows a top elevation of the tool in its compact form as it would be lowered into the oil well string. 
         FIG. 2  shows a side elevation of the tool with the centralising fingers  26 A and  26 B at either end of the tool deployed. 
         FIG. 3  shows a detailed view of the left hand end of the tool within rectangle A of  FIG. 1 . 
         FIG. 4  shows a detailed view of the right hand end of the tool within rectangle B of  FIG. 1 . 
         FIG. 5  shows a detailed view of the left hand end of the tool within rectangle C of  FIG. 2   
         FIG. 6  shows a detailed view of the right hand end of the tool within rectangle D of  FIG. 2 . 
         FIG. 7  shows an end elevation of  FIG. 1  as viewed from the left. 
         FIG. 8  shows an end elevation of  FIG. 2  as viewed from the left. 
         FIG. 9  shows an end elevation of  FIG. 1  as viewed from the right. 
         FIG. 10  shows an end elevation of  FIG. 2  as viewed from the right. 
         FIG. 11  shows a top elevation of the tool with the centralising fingers deployed and with the depth measuring probe  40  deployed. 
         FIG. 12  shows a section E-E through  FIG. 11 . 
         FIG. 13  shows a detail of section E-E as contained by rectangle F in  FIG. 12 . 
         FIG. 13A  shows a close up detail of  FIG. 13  as contained by circle H. 
         FIG. 14  shows a detail of section E-E as contained by rectangle G in  FIG. 12 . 
         FIG. 15  shows a section E-E through  FIG. 11  with detail rectangles J, K and L. 
         FIG. 16  shows a detail of section E-E as contained by rectangle J in  FIG. 15 . 
         FIG. 17  shows a detail of section E-E as contained by rectangle L in  FIG. 15 . 
         FIG. 18  shows a detail of section E-E as contained by rectangle K in  FIG. 15 . 
         FIG. 19  shows an isometric view of the tool with the centralising fingers deployed and with the depth measuring probe  40  deployed with carriage  3  half way along its linear traverse in main body  1 . 
         FIG. 21  shows a top elevation of the tool with the centralising fingers deployed and with the depth measuring probe  40  deployed with detail rectangle P and section N-N. 
         FIG. 22  shows the detail contained within rectangle P of  FIG. 21 . 
         FIG. 23  shows partial section N-N of  FIG. 21 . 
         FIGS. 24-27  show the central detail of section N-N with pecker  4  and cable  40  in varying states of deployment. 
         FIG. 28  shows the depth measuring probe fully deployed into a perforation. 
         FIG. 29  shows the detail contained within rectangle Q of  FIG. 28 . 
         FIG. 30  shows the depth measuring probe tip in contact with the wall lining as part of the hole location pecking sequence (described later in this patent application). 
         FIG. 31  shows the detail contained within rectangle R of  FIG. 30 . 
         FIG. 32  shows the depth measuring probe tip in a restricted perforation. 
         FIG. 33  shows the detail contained within rectangle S of  FIG. 32 . 
     
    
    
     DETAILED DESCRIPTION OF THE EMBODIMENTS 
       FIG. 1  shows the tool in its compact form as it would be lowered into the oil well string. The right hand end of the tool has a screw attachment enabling it to be attached to an e-line, i.e. a braided wire line with a built in signal wire for functions such as the supply of electrical power to the device, the receipt of status and positional information from the device to the surface, and the electrical control of the device from the surface. The powering and control of downhole electrical tools from surface equipment through a wireline cable being well known to those skilled in the art. 
       FIG. 2  shows a side elevation of the tool with the centralising fingers  26 A and  266  at either end of the tool in a deployed position. These fingers act so as to centralise the main body of the tool with respect to the oil well lining, with the fingertips  29  firmly gripping the lining wall to provide an axial and radial datum position for the tool. 
       FIGS. 7 and 9  show end views of the tool with the fingers  26 A,  26 B retracted as shown in  FIG. 1 , and  FIGS. 3 and 4  show side views of the lower and upper ends (respectively) of the tool in the same state. It can be seen that with the fingers retracted, the tool has a minimal exterior profile that is suitable for lowering into a typical well. 
       FIGS. 8 and 10 , and  FIGS. 5 and 6 , show views corresponding to  FIGS. 7 ,  9 ,  3  and  4  respectively with the fingers  26 A,  26 B extended. With the tool within a well, these fingers will impinge on the interior walls of the well, allowing the tool to be fixed relative to the well. 
       FIG. 13  shows how the main body of the tool is rotated axially relative to the bore. A motor, gearbox and encoder assembly  16  is fixed by screws  54 B to support tube  21 A. The output shaft  16 B drives finger support shaft  25  via coupling  34 A. Fingers  26 A are linked to finger support shaft  25  by pins  52 C. Finger support shaft  25  is supported by ball bearing  24 A which is held in place by retaining nut  46 A. Clamp plate  38 A retains ball bearing  24 A to support tube  21 A. By this means and by using appropriate control electronics  51 A, the angular position and speed of finger support shaft  25  and fingers  26 A relative to support tube  21 A can be controlled. When the fingers  26 A are deployed, locking these fingers to the wall lining using fingertips  29 , then rotation of motor/gearbox/encoder assembly  16  causes rotation of support tube  21 A relative to the wall lining. Cabling from the electronics module  51 A to motor/gearbox/encoder assembly  16  is not shown for clarity of illustration. 
       FIG. 13  also shows how the fingers  26 A are deployed and retracted. A further motor, gearbox and encoder assembly  32 A is clamped to motor support tube  18 A with screws (not shown). This is in turn fastened to block  22 A clamping bearing  15 A in place. Lead-screw  33 A is retained to bearing  15  with retaining clamp  20 A. Lead-screw  33 A is screwed into lead-screw nut-block  23 A which is clamped to a finger deployment tube  28 A using screws  41 A through spacers  31 A. Gearbox shaft  32 B is clamped to lead-screw  33 A via coupling  34 B. Rotation of the gearbox shaft  32 B will therefore cause linear displacement of lead-screw nut block  23 A, which in turn causes linear displacement of finger deployment tube  28 A. In  FIGS. 13 and 13A , it can be seen that fingers  26 A have cam-followers  27 A attached which bear on annular feature  28  of finger deployment tube  28 A. Axial displacement of finger deployment tube  28 A thus causes angular rotation of fingers  26 A about pins  52 C. By this means, and by using appropriate control electronics  51 A, the linear position and speed of finger deployment tube  28 A and thereby the angular position and speed of fingers  26 A can be controlled. By controlling the torque of motor  32 A, the clamping force of fingertips  29  against the lining wall can also be controlled. The use of cam followers  27 A allows rotation of central support  1  without undue friction occurring, even with large clamping forces between fingertips  29  and the well lining. 
     Fingertips  29  are fastened to fingers  26 A by pins  52 B and  53 . Should there be a failure of the finger deployment motor or its control electronics whilst the fingers  26 A are deployed, pins  53  are designed to shear when tension is applied to the e-line cable, allowing the tool to be extracted. Rollers  30 A supported on pins  52 A fixed to fingers  26 A will ease the removal of the tool. 
     Similarly,  FIG. 14  shows a motor/gearbox/encoder assembly  32 C at the upper end of the tool, that is clamped to motor support tube  18 B with screws (not shown). This is in turn fastened to block  22 B clamping bearing  15 B in place. Lead-screw  33 B is retained to bearing  15 B with retaining clamp  20 B. Lead-screw  33 B is screwed into lead-screw nut-block  23 B, which is clamped to finger deployment tube  28 B using screws  41 B through spacers  31 B. Gearbox shaft  32 D is clamped to lead-screw  33 B via coupling  34 C. Rotation of gearbox shaft  32 D causes linear displacement of lead-screw nut block  23 B which in turn causes linear displacement of finger deployment tube  28 B. It can be seen that fingers  26 B have cam-followers  27 B attached, which bear on an annular feature of finger deployment tube  28 B. Axial displacement of finger deployment tube  28 B causes angular rotation of fingers  26 B about pins  52 D. By this means, and by using appropriate control electronics  51 B, the linear position and speed of finger deployment tube  28 B and thereby angular position and speed of fingers  26 B can be controlled. 
     Rollers  30 B are also fastened to fingers  26 B via pins  52 E. By controlling the torque of motor  32 C, the clamping force of fingertips rollers  30 B against the lining wall can also be controlled. The use of cam followers  27 B allows rotation of central support  1  without undue friction occurring even with large clamping forces between rollers  30 B and the well lining. Should there be a failure of the finger deployment motor or its control electronics whilst the fingers  26 B are deployed, rollers  30 B will ease the removal of the tool. Fingers  26 B are also shaped to ease the transition over edges by presenting a shallow angle to the tool axis. 
     We will now describe the control of the perforation sensor with reference to  FIG. 16  onwards.  FIG. 15  shows the location along the tool of the sections shown in detail in  FIGS. 16 to 18 . 
     In  FIG. 16 , a motor encoder assembly  17 A is clamped to motor support  18 A with screws (not shown). This is clamped in turn to central support  1  with screws  54 E clamping ball bearing  15 C in place. Ball-screw spindle  13 A is clamped to ball bearing  15 C with clamps  19 A and  20 C. Motor shaft  17 B is clamped to ball-screw spindle  13 A via coupling  34 D. Ball-screw nut  12 A is fastened to cable drive tube  8  and the end of ball-screw spindle  13 A is supported by bearing  14 A which is free to slide in cable drive tube  8 . By this means and by using appropriate control electronics  51 A, rotation of motor shaft  17 B causes linear displacement of cable drive tube  8 . 
     Similarly in  FIG. 17  motor encoder assembly  17 C is clamped to motor support  18 B with screws (not shown). This is clamped in turn to central support  1  with screws  54 F clamping ball bearing  15 D in place. Ball-screw spindle  13 B is clamped to ball bearing  15 D with clamps  19 B and  20 D. Motor shaft  17 D is clamped to ball-screw spindle  13 B via coupling  34 E. Ball-screw nut  12 B is fastened to carriage drive tube  2 , and the end of ball-screw spindle  13   b  is supported by bearing  14   b  which is free to slide in carriage drive tube  2 . By this means and by using appropriate control electronics  51 B, rotation of motor shaft  17 D causes linear displacement of carriage drive tube  2 . 
     Thus, the cable drive tube  8  and the carriage drive tube  2  can each be moved longitudinally as desired. 
     In  FIG. 18 , cable drive tube  8  is fastened to cable support outer tube  5  by pin  57 . Tapered cable clamp  7  is fastened to cable support outer tube  5  by screws  56 , which when tightened grip cable  40  by virtue of the taper surfaces between tapered cable clamp  7  and the cable support outer tube  5 . Cable support outer tube  5  has an aperture which allows relative motion to occur between cable support outer tube  5  and pecker finger  4  without obstruction. By this means linear motion of cable drive tube  8  causes linear motion of cable  40  and depth measuring probe tip  40 A. The direction of cable  40  is controlled by a curved aperture in pecker  4 , pecker  4  being machined as two mirrored halves allowing such an aperture to be created. As the cable  40  is being pushed to determine perforation depth, the cable is prone to buckling. In order to prevent this, a cable support inner tube  6  fastened to pecker  4  by pin  62  is provided which telescopes inside cable support outer tube, thus minimising buckling clearance. By this means cable  40  can be axially displaced with respect to central support  1 , limited by the length of the aperture machined into cable support tube outer tube  5 , with this axial displacement being translated into a radial displacement by curved aperture in pecker  4 , directly related to the rotation of motor shaft  17 B as controlled by control electronics  51 A. 
     Also in  FIG. 18 , Carriage block  3  is fastened to carriage drive tube  2  by screws  55 A (see  FIG. 22 ). Pecker finger  4  is fastened to carriage block  3  by pin  57  about which it is free to rotate. By this means carriage block  3  can be linearly positioned with respect to central support  1 , limited by the length of the aperture machined into central support  1 , by the rotation of motor shaft  17 D as controlled by control electronics  51 B. 
     It can be seen that linear translation of carriage drive tube  2  combined with an equal linear translation of cable drive tube  8  results in linear translation of carriage block  3 , with no relative radial motion of depth measuring probe tip  40 A with respect to carriage block  3 . A linear translation of cable drive tube  8  on its own (i.e. whilst the carriage drive tube  2  remains stationary) causes radial translation of depth measuring probe tip  40 A. A linear translation of both, but at different speeds and/or in a different direction will cause a combination of linear translation of carriage block  3  and radial translation of depth measuring probe tip  40 A. It can be seen that when depth measuring probe tip  40 A is retracted such that it comes into contact with pecker  4 , then pecker  4  will be rotated about pin  57  retracting pecker  4  into carriage block  3 . 
     It should be appreciated that this invention is intended to operate in a highly pressurised fluid filled environment, and therefore any mechanism that projects into this fluid is subject to these large pressures. It is for this reason that carriage drive tube  2  extends beyond the left hand edge of the aperture in central support  1 , having an equal diameter at both ends. Seals  2 A and  2 B at either end of carriage drive tube  2  result in no net torque being applied to motor/encoder assembly  17 C through ball nut  12 B and ball-screw spindle  13 B due to hydraulic force on carriage drive tube  2 . Similarly, cable drive tube  5  extends into carriage drive tube  2  beyond the aperture in carriage drive tube  2  with seals  5 A and  5 B either side just beyond the aperture in cable drive tube  5 . Cable support inner tube  6 A is unsealed allowing fluid to easily pass through it so that regardless of the position of carriage drive tube  2  and cable drive tube  5 , there is no hydraulic volume change resulting in a hydraulically balanced design. Consequentially, there is no net torque being applied to motor/encoder assembly  17 A through ball nut  12 A and ball-screw spindle  13 A due to hydraulic force on cable drive tube  5 . It can be also seen in  FIGS. 13 and 14  that finger deployment tubes  28 A and  28 B have a common sealing diameter for seals  58 A,  58 B,  58 C and  58 D so there are no net hydraulic forces on finger deployment tubes  28 A and  28 B. 
       FIGS. 19 and 20  provide isometric views of  FIG. 18  for clarity. 
       FIGS. 22 and 23  show plan and sectional detail views of pecker  4  and its measurement system, in the region of the tool indicated by detail P in  FIG. 21 . In  FIGS. 22 and 23 , cable  37  is attached to linear measuring transducer rod  9 A by clamp  37 A. Clamp  10  secures the body of linear measuring transducer  9  to central support  1  by virtue of screws  55 C. In addition, the right hand end of clamp  10  provides constraint with clamp  37 A to spring  39 . Cable anchor  37 B is secured to central support  1  by screw  55 B, thus the cable is always kept in tension due to spring  39 . Cable  37  passes under rollers  11  which are retained to carriage block  3  by pins  61  about which they can rotate. Cable  37  also passes over roller  11 A which is retained to pecker  4  by pin  60  about which it can rotate. As pecker  4  is free to rotate about pin  57 , tension in cable  37  causes pecker to swing out from carriage block  3  if cable  40  is extended. If cable  40  is retracted, such that depth measuring probe  40 A contacts the tip of pecker  4 , then the torque on pecker  4  produced by spring  39  will be overcome and pecker  4  will retract into carriage block  3 . This is shown more clearly in  FIGS. 24 to 27 . As spring  39  is compressed, linear measuring transducer rod  9 A moves relative to linear measuring transducer body  9 B producing a position measurement signal to control electronics  51 A. 
     It can be seen that linear translation of cable drive tube  8  as controlled by motor encoder assembly  17 A controls the angular displacement of pecker  4  whilst depth measuring probe tip  40 A is in contact with pecker  4 . If the depth measuring probe tip  40 A hits a section of the wall lining where there is no perforation, then pecker  4  will not rotate fully and the position reached can be determined by linear measurement transducer  9 . This is shown in  FIG. 25 . 
     If the depth measuring probe tip  40 A hits a section of the wall lining where there is a perforation, then pecker  4  will rotate fully and the cable will be deployed into the perforation. If the perforation is sufficiently deep, then the cable will be extended to full depth as determined by the aperture length of the cut-out in cable drive outer tube  5 . Pecker  4  will remain at its angular displacement limit. This is shown in  FIG. 26 . 
     If the depth of the perforation is limited, then the cable will be deployed into the perforation until depth measurement probe tip reaches an obstruction. At this point further cable extension will result in a back thrust on pecker  4  causing it to retract into carriage block  3 . This can be detected by linear measurement transducer  9 , and by an increase in motor torque from motor encoder assembly  17 A. Retracting cable  40  and re-extending it will confirm that an obstruction has been reached or will result in the obstruction being dislodged. Retraction of pecker  4  as a result of an obstruction being reached is shown in  FIG. 27 . Knowing the linear position of the carriage as measured by the encoder in motor encoder assembly  17 B and the linear position of the cable as measured by the encoder in motor/encoder assembly  17 A will enable the depth of the perforation to be determined. 
     The three pecker/cable states are shown in  FIGS. 28 to 33 . 
     It can be seen that this invention has means to clamp itself to a well lining, rotate and translate a pecking tool to locate perforations and means to deploy a depth measurement probe to determine perforation depth. 
     A further modification to this invention would be to add a rotational motor at the junction between cable drive tube  8  and cable clamp  57  to allow the cable to be rotated about its axis as a means to assist debris removal. In these circumstances, the depth measurement probe tip  40 A may have cutting edges to improve debris removal. 
     It will of course be understood that many variations may be made to the above-described embodiment without departing from the scope of the present invention. 
     Although the present invention has been described with reference to preferred embodiments, workers skilled in the art will recognize that changes may be made in form and detail without departing from the spirit and scope of the invention.