EP0208770B1 - Moyen fluide de transmission de donnees - Google Patents

Moyen fluide de transmission de donnees Download PDF

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Publication number
EP0208770B1
EP0208770B1 EP86900913A EP86900913A EP0208770B1 EP 0208770 B1 EP0208770 B1 EP 0208770B1 EP 86900913 A EP86900913 A EP 86900913A EP 86900913 A EP86900913 A EP 86900913A EP 0208770 B1 EP0208770 B1 EP 0208770B1
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EP
European Patent Office
Prior art keywords
fluid
drive
piston
pump
pressure
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EP86900913A
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German (de)
English (en)
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EP0208770A1 (fr
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J.C. Birdwell
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Priority claimed from US06/692,319 external-priority patent/US4676724A/en
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Priority to AT86900913T priority Critical patent/ATE62321T1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B47/00—Survey of boreholes or wells
    • E21B47/12—Means for transmitting measuring-signals or control signals from the well to the surface, or from the surface to the well, e.g. for logging while drilling
    • E21B47/14—Means for transmitting measuring-signals or control signals from the well to the surface, or from the surface to the well, e.g. for logging while drilling using acoustic waves
    • E21B47/18—Means for transmitting measuring-signals or control signals from the well to the surface, or from the surface to the well, e.g. for logging while drilling using acoustic waves through the well fluid, e.g. mud pressure pulse telemetry
    • E21B47/24—Means for transmitting measuring-signals or control signals from the well to the surface, or from the surface to the well, e.g. for logging while drilling using acoustic waves through the well fluid, e.g. mud pressure pulse telemetry by positive mud pulses using a flow restricting valve within the drill pipe

Definitions

  • the present invention is directed to a method of transmitting signals through a flowing fluid, according to the precharacterising part of claim 1. Furthermore, the present invention is directed to a non-pulsating, reciprocating piston type hydraulic pump as use in the method.
  • the non-pulsating, reciprocating piston type hydraulic pump is directed to a means to transmit recorded data from an instrument located in an oil well sub-surface drill string to a surface recording means, the transmission occurring through the circulation fluid medium employed to assist in drilling the well.
  • a surface recording means employed to assist in drilling the well.
  • various recording instruments are placed in the drill string generally near the drill bit to log this different data. It is also desirable to transmit this data to the surface while the well is being drilled. This transmission of data to the surface during drilling is a difficult process because of numerous transmission problems that have to be overcome.
  • the most successfull means of transmitting these signals to the surface presently consists of magnification of the logged data by batteries or other means and employing the data to create pressure pulses in the circulating drilling fluid medium, the pulses generally being created by valve means either momentarily restricting the flow of drilling fluid or momentarily dumping a part of the flow of drilling fluid.
  • the pressure pulses in turn travel through the drilling fluid to the surface where they are received by a recording instrument.
  • a pressure pulse detection apparatus which is adapted to receive small signals from down hole measuring while drilling apparatus which signals are propogated as pressure pulses travelling upstream in a column of drilling mud.
  • This pressure pulse detection incorporates a transient pressure transducer and an ultrasonic fluid velocity detector, the two forming output signals which are conditioned, implified and offset against one another.
  • a hydraulic power convertor comprising fluid driven drive piston means, each of said means having a first side and a second side, each said drive piston means being housed in a separate drive cylinder means, wherein each said drive piston means may receive a continuous flow of pressurized drive fluid to displace a driven piston means within said drive cylinder means.
  • a rotary driven, pressure intensification source to supply the said continuous flow of pressurized drive fluid is provided, said source having a pressurized fluid outlet and a lower pressure fluid inlet.
  • said drive piston means transmitting an output drive motion.
  • an object of the present invention to provide a method of transmitting signals through a flowing fluid, according to the precharacterising part of claim 1 in which the drilling fluid pressure is held relatively constant by eliminating the necessity to send pressure pulses through the fluid medium.
  • a further object of the present invention is to provide a non-pulsating, reciprocating piston type hydraulic pump which is used in the method of the present invention.
  • the method of this invention employs the technique of holding the drilling fluid pressure relatively constant thus varying the flowing of the drilling fluid and recording the various fluids at the surface.
  • this technique the same type down hole logging tools and down hole signalling devices are employed, except the signalling device will in turn change the flow rate of the drilling fluid which in turn is recorded at the surface thus eliminating the necessity to send pressure pulses through the fluid medium.
  • Fig. 1 where the numeral 10 generally identifies a hydraulic driven pump that has the capability to create and sustain a constant pressure pumped fluid system.
  • the numeral 11 generally pumped fluid system.
  • the numeral 11 generally identifies a drilling fluid circulating system circulating drilling mud through a pumping cylinder 12, a drill string 13, a down hole logging device 14, a drill bit 15, a bore hole 16, and a mud reservoir 17.
  • Pumping cylinder 12 is one of generally three pumping cylinders of the pump illustrated by the numeral 10.
  • the circulating fluid which generally is a weighted drilling mud, is drawn from reservoir 17 through line 18 and into the pumping chamber at 19.
  • a reciprocating piston 20 driven by rod 21 discharges fluid from a chamber 23 across unidirectional outlet valve 22 as piston 20 moves in one direction on its power stroke.
  • Piston 20 next moves on its return stroke at which time the fluid is transferred from chamber 24 to chamber 23 moving across one or more unidirectional valves 25 carried in movement by piston 20.
  • a small amount of fluid equal to the rod 21 area in volume will be drawn into chamber 23 from reservoir 17 as piston 20 moves in return stroke.
  • Pump 10 can function with two or more cylinders 12 to provide constant pressure pumping, however the preferred embodiment employs three or more cylinders 12.
  • Inlet line 18 is connected in parallel to all cylinders 12 and the drill string 13 is connected in parallel to the outlet of all cylinders 12.
  • the piston 20 of all cylinders 12 are driven in sequential order and overlapping drive movement whereby the total output flow from all cylinders 12 is uniform in constant volumetric flow for a given fluid displacement.
  • Each piston rod 21 is driven in pumping movement with a constant force which in turn creates a constant pressure in chamber 23 and in the circulating fluid passing through drill string 13. The means to drive piston rod 21 with a constant force will be discussed later.
  • Logging device 14 can be any number of different down hole monitoring systems, it can be a device to monitor or log the different earth formations, the down hole temperature, bit rotation, bit inclination, etc. These devices generally employ highly sophisticated and complex means to pick up a signal, magnify the signal and then transmit the signal into movement of some type of plunger or valving device such as plunger 26 to restrict a typical orifice 27 through which the circulating fluid flows. This technique is well known by those versed in the art. In the present state of the art, this or similar means are employed to create pressure pulses in circulating fluid to transmit data to the surface.
  • the signal produced by the logging device can be instantly interpreted at the surface location.
  • the drill bit In the drilling of wells, the drill bit is generally rotated by some type of down hole motor located near the bit such as 29, or the complete drill string is rotated from a surface rotary table which, naturally requires a swivel of some type in the drill string above the rotary table.
  • the rotary table and swivel are omitted for clarity purposes as their functions obviously have no bearing upon this data transmission means.
  • the down hole motor 29 is illustrated as located in a position above the logging instrument 14. Motor 29 could also be located at a point below instrument 14 if desired. It is generally desirable to have the logging instrument located as close as possible to the drill bit; for example if the instrument is logging a potential oil bearing formation, then it is desirable to have data transmitted to the surface as soon as possible after the drill bit enters the formation. Thus it is advantageous to be able to locate the logging instrument below the motor and still transmit signals.
  • Motor 29 is generally a motor driven by the circulating fluid.
  • the transmission of signals will cause a change in speed of a down hole motor driven by the circulating fluid but there should be no appreciable interference with signal transmission whether the motor is above or below the logging device.
  • logging device 14 can be utilized to speed up or slow down the rotation of down hole motor 29 by increasing or decreasing the flow rate of the circulating fluid passing through the motor 29.
  • instrument 14 allows for the instrument to pick up its signals from many and various different sources, thus any of these various sources can be utilized to in turn control the rotation speed of motor 29 that is driven by the circulating fluid.
  • instrument 14 may be programmed to close orifice 27 upon a given temperature or pressure thus stopping motor 29; or instrument 14 may be programmed to enlarge orifice 27 thereby increasing the drilling speed of motor 29 when a particular type earth formation is encountered.
  • the constant pressure circulating fluid system of transmitting signals may also provide automatic down-hole motor speed control capabilities, or the transmitting of signals from a first to a second or more down hole instruments.
  • Fig. 1 of the drawings where the numeral 10 generally identifies the hydraulicly driven pump utilized to create the constant pressure circulating fluid system illustrated by numeral 11.
  • Numeral 10 generally illustrates a hydraulically driven cylinder 30 having a reciprocating drive piston 31 drivingly connected on one side to piston rod 21 and having on its other side a rod 32 sealingly extended through the end of cylinder 30.
  • Each pumping cylinder 12 is driven by a cylinder 30.
  • Rod 32 has a larger cross section area than a rod 21 so that equal pressure upon both faces of piston 31 will move piston 31 in the direction of rod 32.
  • Rod 32 and piston 31 define an expansionable drive fluid chamber 33 on one side of piston 31, and rod 21 and piston 31 defines a part of an expansionable return fluid chamber 34 on the other side of piston 31.
  • a fluid port at 37 is fluidally connected to chambers 34 of all other drive cylinder 30 to form an interconnected chamber 34 common to all cylinders 30.
  • Constant pressure hydraulic drive fluid is connected with each drive chamber 33 in sequential and overlapping turn to move or not to move piston 31 in pressured circulating fluid displacement or non displacement _ the circulating fluid displacement being dependent upon the opening size of orifice 27.
  • orifice 27 allows fluid to circulate then the drilling fluid will circulate with a volumetric flow rate relative to the orifice flow area. If orifice 27 allows no flow to pass therethrough, then the circulating fluid will be in static movement with a constant applied pressure.
  • This fact can be especially useful in checking leakage of the threads of the different joints of drill pipe employed in the drill string. Also this can be employed to check each tool joint thread as the drill string is being lowered into the hole by having orifice 27 in a closed position and checking each joint after the joint is added to the drill string.
  • a typical orifice 27 could be programmed to permanently release after the drill bit reaches bottom and then continue other transmission.
  • constant pressure circulating fluid can be utilized to check for leakage of added tool joint threads during drilling operations by the technique of noting the flow rate of fluid crossing plane 28 immediately prior to lowering circulating pressure for adding the next tool joint. After the joint is added and pressure is resumed, then an increase in the noted flow rate would indicate a leakage of the threads just added _ assuming orifice 27 does not change in size.
  • each chamber 33 not connected with the hydraulic drive fluid is connected with chamber 34 and with a low pressured hydraulic fluid supply system to a hydraulic drive pump 35 that supplies the constant pressured hydraulic drive fluid.
  • the sequential and in turn connection between chambers 34 and each chamber 33 is accomplished by a valving means 36 that will be explained later, this connection provides the same low pressure fluid upon both faces of piston 31 thus due to the difference in piston 31 face areas because of rod 32 and rod 21, piston 31 is moved in the return direction of movement
  • the primary source of piston 31 return movement is supplied by one or more drive pistons 31 moving in the drive direction which displaces fluid from one or more chambers 34 through interconnected ports 37.
  • One or more pistons 31 moving in drive movement will in turn drive other pistons 31 in return movement through interconnected fluid chambers 34.
  • a secondary source of return piston movement is supplied by a system charge pump 38 connecting with chambers 34 and the inlet of hydraulic pump 35 to keep chambers 34 and the inlet line to pump 35 in a precharged pressured state.
  • a relief valve 39 also connects with chambers 34 and the inlet line to pump 35. Valve 39 exhausts excess fluid to a hydraulic reservoir 40.
  • the relief valve 39 is adjusted to bypass fluid to reservoir 40 whenever the fluid in chambers 34 reach a pressure slightly higher than the pressure required to drive piston 31 in the return direction. This setting cannot be exactly calculated and should be determined after assembly of cylinder 12 and 30. Each assembly of cylinders 12 and 30 will require slightly different chamber 34 piston 31 return pressure due primarily to difference in frictional drag, thus valve 39 must be set to relieve fluid at a pressure higher than the piston 31 return pressure of all cylinders 12 and 30 assemblies.
  • the combined total volume of chambers 34 continually expands and contracts.
  • the volume will expand as long as any piston 31 is free to move unrestrictedly in the return direction.
  • the volume will contract when all returning pistons reach the end of their stroke and a driving piston 31 raises the pressure in chamber 34 to the relief valve 39 setting to exhaust excess fluid.
  • This exhausting process normally occurs upon each piston 31 return stroke, except when the stroke length of piston 31 is shortened.
  • the stroke length of piston 31 is shortened during pumping operation, then all pistons 31 will move toward the return direction in shortened stroke length. The dumping of excess fluid does not occur during this movement as all chambers 34 are in the process of expansion.
  • One piston 31 may assume a position of reciprocation near the drive end stroke of cylinder 30, a second piston 31 may assume a position of reciprocation near the return end of cylinder 30, and third piston 31 may be reciprocating at a point anywhere along the length of cylinder 30. Since this occurs it means that once the pistons have assumed skew positions of relative reciprocation it is impossible to again increase the stroke length without at least one drive piston 31 hitting the end of its stroke too soon, thereby interrupting the continuity of the constant drive action of pistons 31. In the device disclosed in Smith, skewed piston position would lock up the disclosed system because the disclosed valve movement is timed with and dependent upon piston movement.
  • the device disclosed in Smith may be characterized by prohibitive and destructive pressure surges in both the hydraulic drive fluid and the pumped circulating fluid upon a piston 31 reaching the end of its stroke too soon. Additionally, the above described skewed piston positions will normally prohibit starting of stopped pistons 31 without encountering the same premature stoppage of pistons 31. Thus from the above discussion it will be apparent that the continued expansion of chambers 34 is necessary to achieve an uninterrupted constant pressured pumping action.
  • the pistons 31, on their return strokes will always return at a velocity greater than the velocity with which they are displaced on their drive strokes because of the charge pump 38. By returning the pistons at a greater velocity it is impossible for the drive piston movement and the return piston movement to be in the same timed movement as has been heretofore disclosed by Smith.
  • the normal movement of drive piston 31 is in sequential turn and overlapping constant displacement movement to supply the same movement to pumping piston 20. This mandates that the normal movement of return pistons 31 will be a sequentially interrupted overall movement, if there is an overlap in the return pistons movement it will be for all practical purposes of a non-existent magnitude. Thus, for all practical purposes, the return movement of pumping pistons 20 are non overlapping in overall movement.
  • the unidirectional valves 25 carried in movement by pumping pistons 20 provide an arrangement whereby the majority of the pumped circulating fluid is drawn to cylinder 12 during the movement of the displacement stroke of piston 20.
  • the displacement movement is overlapping and overall constant as pistons 20 reciprocate; thus by employing the moveable valve 25, means is disclosed for cylinder 12 to both receive a substantial constant flow of incoming fluid and to discharge a constant flow of pumped fluid.
  • the incoming suction flow would be stopped upon each return stroke movement as the return strokes have essentially zero overlap.
  • FIG. 1 where the numeral 10 illustrates a closed loop hydraulic system combined with an independently sequenced valving system to drive cylinder 30 as discussed.
  • Variable volume hydraulic pump 35 is driven by a motor 41 to supply pressured hydraulic fluid through line 42 to distribution valve 36.
  • Valve 36 is driven by a motor 43 to distribute pressured hydraulic fluid through lines 45 in a continuous uninterrupted fashion in sequential turn and overlapping manner to chambers 33 of drive cylinders 31.
  • Valve 36 also returns spent pressured fluid in sequential turn from chambers 33 to lower pressured return line 44 connecting with chambers 34 and the inlet to pump 35.
  • the pressured fluid is distributed by valve 36 to a single chamber 33 for a substantial part of piston 31 drive movement; and then, near the end of piston 31 stroke, the fluid is switched to start another piston 31 in overlapping drive movement.
  • the return portion of valve 36 simultaneously connects all chambers 33 that are not receiving drive fluid with the return line 44 for return piston 31 movement.
  • Charge pump 38 driven by motor 41, keeps the closed loop pre-charged with pressurized fluid through check valves 46 or 47.
  • the pumped circulating fluid within drill string 13 is maintained in constant pressure status by maintaining a constant drive fluid pressure against drive pistons 31.
  • This is accomplished by a relief valve 48, a check valve 49, a small orifice 50, and a lock valve 51.
  • Relief valve 48 serves several different functions. The main function is to limit the maximum pressure upon line 42, which is an essential function since hydraulic pump 35 is a positive displacement type pump. Pressure is relieved from line 42 to a line 52 then across check valve 49 to low pressure line 44.
  • Valve 48 can be any type of relief valve but it is preferred that it be a type that can be remotely controlled from a pressure line 53 whereby valve 48 relieves flow to line 52 at the pressure that is held upon pilot line 53. This type of hydraulic relief valve is well known in the art thus a complete discussion of its operation is not necessary. This type of valve can also generally be controlled by a maximum pressure manually set and controlled anywhere below this maximum setting by the pressure held upon pilot 53.
  • Pump 35 is preferably a piston type pump employing a moveable swash plate that is controlled by two swash plate pistons.
  • a typical pump 35 thus would have zero pumping displacement when the swash plate is held in a vertical plane relative to piston movement, with the swash plate being moved from the vertical plane for pumping displacement by two swash plate pistons.
  • a remote control lever of some type generally commands the swash plate pistons to position the swash plate for pumping action anywhere from zero to maximum displacement.
  • a typical pump of this type is a pump employed as the pump part of a typical hydraulic hydrostatic drive unit. These pumps are well known in the art and thus complete explanation of their operation is not necessary.
  • a line 54 connects one swash plate piston of pump 35 with line 52 through a lock valve 51.
  • the other swash plate piston is connected by a line 55 to reservoir 40 through lock valve 51.
  • the swash plate piston that is connected to line 55 must be the piston that is pressured to hold the swash plate in pumping displacement.
  • the drive fluid line 42 is held in constant drive pressure in the following manner: valve 48 is set to relieve fluid at the selected constant drive pressure, pump 35 is ordered to pump maximum flow; thus when the selected pressure is reached, a bypass flow crosses valve 48 and enters line 52.
  • Check valve 49 has a spring tension to maintain a pressure differential of generally about 50 PSI (3,5 kp/cm2) upon line 52 or as required to move the swash plate piston of pump 35. This pressured fluid within line 52 flows through lock valve 51 and then through line 54 and to the swash plate piston to reduce the pumping displacement of pump 35.
  • a flow meter 56 located on the suction side of pump 35 measures the flow of hydraulic oil pumped through pump 35.
  • This flow meter can also be used to gauge the flow of pumped, constantly pressured and circulating fluid which passes through pumping cylinders 12 since the flow of pumped circulating fluid is directly proportional to the flow of hydraulic drive fluid passing through pump 35.
  • a unique system is employed in hydraulic flow control, consisting of a compressible gas filled accumulator 57, a variable volume orifice 58, and a check valve 59.
  • orifice 58 is set to admit a small flow to accumulator 57 from line 42.
  • the line connecting accumulator 57, orifice 58, and check valve 59 is connected to the remote control line 53 of valve 48.
  • Check valve 59 is positioned to block flow to accumulator 57, but to rapidly exhaust flow from accumulator 57.
  • a rotary spool 60 is rotatably and sealingly encased within a housing 61.
  • Housing 61 has inlet port 62 that leads inward to grove 63 around the circumference of spool 60.
  • Grove 63 connects through ports 64 to a crossport 65 leading through spool 60.
  • Crossport 65 is formed to mate in rotational movement and in successive overlapping turn with multiple ports 66 formed around the circumference of housing 61.
  • Leading from each port 66 is a connecting port 67 that connects in successive turn with a second crossport 68 leading through spool 60.
  • Crossport 68 is located at 90 degrees spacing from crossport 65 and sized so that crossport 68 and crossport 65 never overlap for direct fluid flow therebetween.
  • Crossport 68 connects to an outlet port 69 through a port 90.
  • pressured drive fluid from line 42 enters valve 36 at inlet port 62. From there it flows through groove 63, ports 64 and then is delivered in sequential and overlapping turn to lines 45 through ports 66 to drive piston 31 displaced in its drive stroke. Simultaneously, crossport 68 connects in sequential turn all ports 66 not receiving drive fluid to exhaust spent drive fluid to lower pressured return line 44 and to chambers 34, thereby driving other pistons in return movement.
  • Spool 60 is sealingly and rotatably retained within housing 61 by end plates 70 and 71.
  • End plate 70 is attached to housing 61 by bolts 72 and has a seal at 73 and supports a thrust bearing 74 that limits end movement of spool 60 in one direction.
  • End plate 71 is attached to housing 61 by bolts 95 and supports a seal at 76 and a thrust bearing 77 that limits end movement of spool 60 in the other direction.
  • End plate 71 has a central opening 78 through which a drive shaft 79 of spool 60 extends. Drive shaft 79 is sealed in static and rotational movement by seal 80.
  • Spool 60 is finely ground to sealingly mate in static and rotational movement with the inner bore of housing 61, additionally circumferential seals are located at 81 on each end of spool 60.
  • the constant pressure pumping system can be created only when typical orifice 27 is small enough in flow area to cause the maximum flow rate of pump 35 to set up a pressure in line 42 that is equal to the relief valve 48 setting.
  • the hydraulicly driven pump illustrated by numeral 10 will operate as a constant displacement pump wherein a reduction in orifice 27 size will cause a rise in pumped circulating fluid pressure.
  • valve 75 can be connected with relief valve 48 pilot line 53, whereby the pressured fluid bypass setting of valve 48 can be remotely changed by changing the maximum relief setting of valve 75.
  • Valve 75 is generally located in some type of control panel and can provide a means to easily adjust the drive circuit 42 pressure whereby the hydraulicly driven circulating fluid pump can selectively function for constant pressure or constant flow pumped output.
  • the constant flow or constant pressure pumping modes may also be automatically selected by the down hole logging instrument 14.
  • two or more orifices 27 may be employed whereby the combined areas of all orifices give a total flow area large enough so that the maximum flow rate of pump 35 will not set up the bypass pressure requirement of valve 48. Therefore the hydraulicly driven pump will pump fluid in the constant flow mode whereby signals can be transmitted by pressure pulses
  • instrument 14 can be programmed to close some of the orifices 27 upon receipt of a given signal whereby, the orifices closed, then the overall area of orifice 27 is small enough so that the hydraulicly driven pump will automatically operate in the constant pressure pumping mode.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Geology (AREA)
  • Geophysics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Remote Sensing (AREA)
  • Acoustics & Sound (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Dans un moyen pour transmettre des données enregistrées par l'intermédiaire d'un milieu fluide, le mode préférentiel de réalisation comporte une pompe volumétrique hydraulique (10) reliée à une pompe sous pression constante (12) qui pompe du fluide à travers un train de tiges (13) pour forer des puits de pétrole. Un orifice variable (27) est situé au fond du puits dans le train de tiges (13) et son diamètre se modifie en fonction des signaux enregistrés. Le fluide injecté est déplacé par un piston (20) de refoulement entraîné par un second piston (31), lequel est actionné par un fluide hydraulique sous pression constante. Le fluide injecté est maintenu à une pression constante, par conséquent une variation du diamètre de l'orifice (27) va modifier le volume d'écoulemtn à travers l'orifice et de ce fait modifier le volume d'écoulement du fluide hydraulique d'actionnement. Le débit de ce dernier est ainsi mesuré pour enregistrer les variations du diamètre de l'orifice et en échange recevoir les signaux émis par la variation du diamètre de l'orifice.

Claims (10)

1. Un procédé de transmission de signaux par l'intermédiaire d'un fluide s'écoulant dans un conteneur fermé constitué d'une longueur de tuyau dans un trou de forage, caractérisé par les étapes suivantes:
capter le fluide à l'intérieur dudit conteneur fermé ayant un orifice d'écoulement de sortie (27), ledit orifice d'écoulement de sortie étant situé en bas du trou;
ajouter le fluide audit conteneur à une vitesse égale à la vitesse dudit fluide s'échappant dudit conteneur;
imposer une pression constante sur ledit fluide au moyen d'une pompe hydraulique du type à piston alternatif, non pulsatoire multiple entraînée par le fluide d'entraînement constamment sous pression, dont la vitesse d'écoulement volumétrique est directement proportionnelle à la vitesse d'écoulement volumétrique dudit fluide ajouté audit fluide capté; mesurer les données sélectionnées en bas du trou et convertir la mesure en un signal;
ledit signal induisant un changement de la taille dudit orifice d'écoulement de sortie (27) provoquant un changement de la vitesse d'écoulement volumétrique dudit fluide s'échappant dudit conteneur, où de ce fait le changement de ladite vitesse d'écoulement dudit fluide s'échappant dudit conteneur et dudit fluide ajouté dans ledit conteneur fournit le moyen de transmission dudit signal;
mesurer et enregistrer le changement de la vitesse d'écoulement dudit fluide ajouté audit conteneur en un emplacement à la surface.
2. Le procédé selon la revendication 1 caractérisé en ce qu'une fuite dans le système de circulation constamment sous pression est décelable à chaque fois que ledit orifice (27) est fermé en surveillant la vitesse d'écoulement dans un plan (28).
3. Une pompe hydraulique du type à piston alternatif non pulsatoire telle que celle utilisée dans le procédé de la revendication 1 ou 2, ladite pompe comprenant:
les moyens de piston d'entraînememnt entraîné par le fluide (31), chacun desdits moyens ayant un premier côté et un second côté, chacun desdits moyens de piston d'entraînement (31) étant logés dans un moyen de cylindre d'entraînement séparé (30), où chacun desdits moyens de piston d'entraînement (31) peut recevoir un écoulement continu du fluide d'entraînement sous pression pour déplacer lesdits moyens de piston d'entraînement (31) à l'intérieur dudit moyen de cylindre d'entraînement (30);
une source d'intensification de pression entraînée de façon rotatoire pour alimenter ledit écoulement continu du fluide d'entraînement sous pression, ladite source ayant un orifice de sortie du fluide sous pression et un orifice d'arrivée inférieure du fluide sous pression;
lesdits moyens de piston d'entraînement (31) transmettant un mouvement d'entrainement de sortie;
caractérisé en
ce que pendant l'opération, au moins l'un desdits moyens d'entraînement (31) sera déplacé dans un premier sens d'entraînement à l'intérieur desdits moyens de cylindre (30) tout le temps, alors que lesdits moyens de piston d'entraînement (31) seront périodiquement déplacés dans un second sens de retour à l'intérieur de chacun desdits moyens de cylindre (30); en ce que le moyen de soupape de contrôle (36) est prévu, pour relier, indépendamment de la position ou du mouvement du piston d'entraînement, mais de façon séquentielle, ladite source d'intensification de pression du fluide à sa sortie par étapes et chaque moyen de cylindre d'entraînement (31) l'un après l'autre, et pour relier l'autre moyen de cylindre d'entraînement (31) à ladite source d'intensification de pression du fluide à son arrivée pour entraîner continuellement de ce fait un ou plusieurs moyens de piston d'entraînement (31) dans ledit premier sens d'entraînement, de façon séquentielle et l'un après l'autre et en se chevauchant;
en ce qu'un circuit de fluide de dilatation captant un second fluide sous pression à l'intérieur desdits moyens de cylindre d'entraînement (30) d'un premier côté desdits moyens de piston d'entraînement (31); où de ce fait le mouvement d'un ou plus desdits moyens de piston d'entraînement (31) dans ledit premier sens déplace à son tour l'autre deddits moyens de piston d'entraînement (31) dans le second sens de retour;
un moyen pour ajouter continuellement du second fluide sous pression audit circuit de fluide de dilatation pour provoquer une dilatation de celui-ci, et un moyen pour évacuer le fluide en excès dudit circuit de fluide de dilatation automatiquement au moment d'une augmentation donnée de la pression à l'intérieur; et dans lequel, ladite source d'intensification de pression du fluide fournit un fluide d'entrainement sous pression directement à l'un desdits moyens de cylindre d'entraînement (30) et de ce fait le fluide d'entraînement utilisé sous pression inférieure est renvoyé à ladite entrée de ladite source d'intensification de pression du fluide à partir d'un ou plus desdits moyens de cylindre d'entraînement (30).
4. La pompe selon la revendication 3 comprenant un moyen pour varier le volume dudit premier fluide sous pression fourni à ladite soupape de contrôle (36) pour de ce fait varier la distance selon laquelle chaque piston (31) est déplacé à l'intérieur de son cylindre respectif (30) dans ledit premier sens.
5. La pompe selon la revendication 3 ou 4 comprenant des moyens (43) pour varier la vitesse opérationnelle de ladite soupape de contrôle (36) pour varier la distance chaque piston (31) est déplacé dans ladite première direction et comprenant des moyens pour ajouter ou retirer ledit second fluide sous pression dans ledit circuit de fluide de dilatation pour compenser ledit changement du volume dudit second fluide dû à ladite différence de distance de déplacement.
6. La pompe selon l'une des revendications 3 à 5 dans laquelle ledit circuit de fluide de dilatation est reliée à un troisième conduit transférant ledit premier fluide évacué à partir de ladite soupape de contrôle.
7. La pompe selon l'une des revendications 3 à 6 dans laquelle le fluide est ajouté audit circuit de fluide de dilatation par ladite première source de fluide sous pression (35).
8. La pompe selon l'une des revendications 3 à 7 dans laquelle chacun desdits pistons (31) est relié à un moyen de pompage de fluide de déplacement positif alternatif (12) ayant une première extrémité et une seconde extrémité, ladite première extrémité de chaque tige (21) étant reliée à un piston séparé, ladite seconde extrémité de ladite tige de connexion (21) étant reliée audit moyen de pompage; et comprenant un moyen pour entraîner ladite soupape de contrôle (36) indépendement de la position et du mouvement du piston.
9. La pompe selon la revendication 8 dans laquelle ledit moyen de pompage du fluide (12) comprend des soupapes unidirectionnelles (25) et un moyen de pompe à piston alternatif (20) où de ce fait ledit moyen de pompage (12) déplace le fluide et reçoit le fluide lorsque lesdits pistons (20) de ladite pompe sont déplacés dans ladite première direction pour créer de ce fait une action de pompage non-interrompue du fluide par l'intermédiaire dudit moyen de pompage.
10. La pompe selon la revendication 9 dans laquelle ledit moyen de pompe à piston alternatif (20) est enfermé en coulissant et de manière étanche dans une chambre de pommpage au moyen d'une colonne remplaçable.
EP86900913A 1985-01-16 1986-01-15 Moyen fluide de transmission de donnees Expired - Lifetime EP0208770B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86900913T ATE62321T1 (de) 1985-01-16 1986-01-15 Spuelungsmittel fuer datenuebertragung.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US06/692,319 US4676724A (en) 1981-10-08 1985-01-16 Mud pump
US692319 1985-01-16
US76242685A 1985-08-05 1985-08-05
US762426 1985-08-05

Publications (2)

Publication Number Publication Date
EP0208770A1 EP0208770A1 (fr) 1987-01-21
EP0208770B1 true EP0208770B1 (fr) 1991-04-03

Family

ID=27104945

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86900913A Expired - Lifetime EP0208770B1 (fr) 1985-01-16 1986-01-15 Moyen fluide de transmission de donnees

Country Status (5)

Country Link
EP (1) EP0208770B1 (fr)
AU (2) AU590251B2 (fr)
BR (1) BR8604538A (fr)
CA (1) CA1275181C (fr)
WO (1) WO1986004383A2 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117705218B (zh) * 2024-02-06 2024-04-16 江苏省计量科学研究院(江苏省能源计量数据中心) 一种加油机计量数据在线测量的系统及方法

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB767325A (en) * 1953-07-15 1957-01-30 Imo Industri Ab Improvements in or relating to hydraulic pump systems
GB833912A (en) * 1958-07-08 1960-05-04 Maquinaria Petrolifera S A Liner and packing for reciprocating piston pumps
DE2147984C3 (de) * 1971-09-25 1975-05-07 Hellmuth Walter Gmbh, 2300 Kiel Steuervorrichtung für einen Druckflüssigkeits-Schubkolbenmotor
DE2147985A1 (de) * 1971-09-25 1973-03-29 Scharmann & Co Waagerecht-bohr- und fraeswerk mit einem an fuehrungen auf- und abwaerts bewegten spindelkasten
US4076457A (en) * 1976-09-17 1978-02-28 Standard Oil Company (Indiana) Downhole pump speed control
US4262343A (en) * 1979-04-18 1981-04-14 Dresser Industries Pressure pulse detection apparatus
GB2137260B (en) * 1980-08-27 1985-04-11 Sperry Sun Inc Improvements in or relating to apparatus for signalling within a borehole while drilling
EP0075618A1 (fr) * 1981-09-25 1983-04-06 HARBIDGE, John Arrangement de contrôle d'un circuit de fluide sous pression
US4562560A (en) * 1981-11-19 1985-12-31 Shell Oil Company Method and means for transmitting data through a drill string in a borehole
WO1983001983A1 (fr) * 1981-11-25 1983-06-09 Box, Frederick, James Systemes a pompe
BR8507113A (pt) * 1984-12-12 1987-03-31 J C Birdwell Bomba de lama

Also Published As

Publication number Publication date
WO1986004383A2 (fr) 1986-07-31
AU4120389A (en) 1989-12-21
AU590251B2 (en) 1989-11-02
AU5355886A (en) 1986-08-13
CA1275181C (fr) 1990-10-16
EP0208770A1 (fr) 1987-01-21
WO1986004383A3 (fr) 1986-09-12
BR8604538A (pt) 1987-07-14

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