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EP3574214B1 - Wobble pump comprising a wobble plate - Google Patents

Wobble pump comprising a wobble plate Download PDF

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Publication number
EP3574214B1
EP3574214B1 EP18700369.4A EP18700369A EP3574214B1 EP 3574214 B1 EP3574214 B1 EP 3574214B1 EP 18700369 A EP18700369 A EP 18700369A EP 3574214 B1 EP3574214 B1 EP 3574214B1
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EP
European Patent Office
Prior art keywords
pump
drive shaft
plate
rotary plate
pistons
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP18700369.4A
Other languages
German (de)
French (fr)
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EP3574214A1 (en
Inventor
Julien TROST
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IFP Energies Nouvelles IFPEN
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IFP Energies Nouvelles IFPEN
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Publication of EP3574214A1 publication Critical patent/EP3574214A1/en
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Publication of EP3574214B1 publication Critical patent/EP3574214B1/en
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
    • E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
    • E21B43/121—Lifting well fluids
    • E21B43/126—Adaptations of down-hole pump systems powered by drives outside the borehole, e.g. by a rotary or oscillating drive
    • 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
    • E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • F04B1/148—Bearings therefor
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/16—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or pistons

Definitions

  • the present invention relates to the field of pumps, in particular for high pressure pumping, in particular for drilling operations.
  • crankshaft pumps are the most widespread in all sectors of industry: capital goods, the oil, gas and food industries, the automotive sector, construction (heating, wells, air conditioning, water pumps, etc.) and more specifically for the treatment of water and waste (water and sanitation network).
  • these pumps have limits in terms of power, pressure / flow torque (limited by "water hammers” generated by the sinusoidal pressure of the crankshaft), weight, efficiency and service life.
  • they do not allow variable displacement and therefore lack flexibility of use.
  • Pumps designed with a barrel operate using a turntable system that actuates the different pistons one after the other.
  • the opposite piston is in the discharge mode, which provides a flow constant upstream and downstream of the pump.
  • the distribution of the positions of the pistons with a guide by the barrel ensures a progressive distribution of the forces during the rotation of the shaft driven by the motor.
  • cylinder pumps with variable displacement for which the inclination of the rotary plate is adjustable are described in the patent applications: US 2014/0186196 , US 6,176,684 , US 5,295,796 .
  • the inclination adjustment systems are either a servo-piston, or a system with an electric motor and cams, or a hydraulic system. These systems are complex and are not completely satisfactory.
  • the present invention relates to a barrel pump with a swash plate, for which the angle of inclination of the rotary plate relative to the drive shaft is adjustable by means of a finger ball joint.
  • the inclination of the platform is continuously adjustable, which allows a variable displacement.
  • the pump according to the invention allows good flexibility thanks to the continuous variation of the unit displacement, as well as good reliability thanks to the possibility of progressive start-up of the pump.
  • the embodiment in the form of a barrel pump allows a compact design of the pump.
  • the pump comprises a return rod, said return rod being in a ball joint connection with said housing and said swash plate.
  • the angle of inclination of said rotary plate and of said swash plate relative to the axis of said drive shaft is between 70 and 90 °.
  • said rotary plate comprises a groove in which the finger of said ball joint moves, said groove being substantially parallel to the axis of said drive shaft.
  • said pump comprises means for controlling the inclination of said rotary plate relative to said drive shaft.
  • the energy of said control means comes from a source external to said pump, in particular by means of a pressurized fluid.
  • the energy of said control means is taken from said drive shaft.
  • said cylinder block is fixed relative to said housing.
  • the invention relates to a use of said barrel pump according to one of the preceding characteristics for a drilling operation, in particular for the injection of drilling mud into a wellbore.
  • the present invention relates to a barrel pump with a swash plate.
  • the purpose of the barrel pump is to pump a fluid (for example: water, oil, gas, drilling muds, etc.) by means of a linear displacement of several pistons.
  • This type of pump has the advantage of being compact, of having interesting mechanical and volumetric outputs, an excellent weight / power ratio.
  • barrel pumps with a swash plate are suitable for high pressure pumping.
  • the rotary plate is driven by the drive shaft by means of a finger ball joint, the position of the finger ball joint determining the inclination of the two plates (rotary and oscillating) with respect to the drive shaft.
  • a ball joint with a finger is a connection between two elements (here the drive shaft and the rotary plate), which has four degrees of connection and two degrees of relative movement; only two relative rotations are possible, the three translations and the last rotation being linked.
  • the finger of the ball joint makes it possible to adjust the inclination of the plates relative to the drive shaft.
  • the pump comprises means for controlling the finger ball joint, and therefore the inclination of the plates relative to the drive shaft.
  • the inclination of the rotating and oscillating plates is continuously adjustable, which allows variable displacement.
  • the inclination of the plates influences the stroke of the pistons.
  • the pump according to the invention allows good flexibility thanks to the continuous variation of the unit displacement.
  • the pump according to the invention allows good reliability thanks to the possibility of gradually starting the pump: for example, during start-up, the angle of inclination may be small, and subsequently, it may be increased according to the desired conditions (flow rate and pressure of the fluid). This reliability cannot be obtained with a pump whose inclination of the plates is fixed, or for which the inclination cannot vary continuously.
  • the trays may have substantially the shape of a disc. However, the trays can have any shape. Only the compression chambers (and the pistons) are distributed in a circle.
  • the pump according to the invention can include a number of pistons between three and fifteen, preferably between five and eleven.
  • a high number of pistons provides a continuous flow upstream and downstream of the pump.
  • the input rotational movement (drive shaft) is first transformed into an oscillating movement (swash plate) and secondly into a translational movement, i.e. say a back and forth movement (pistons).
  • the reciprocating movement of the pistons in the compression chambers ensures the pumping of the fluid.
  • the pump further comprises an inlet and an outlet for the fluid to be pumped.
  • the fluid passes through the inlet of the pump, enters a compression chamber, is compressed, and then discharged from the pump through the outlet by means of the piston.
  • pivot connections are formed by bearings or bearings, promoting the relative movement of the elements.
  • the inclination can be adjusted by moving the finger of the ball joint in a groove made in the rotary plate, the axis of the groove being able to be parallel to that of the axis rotation of the drive shaft.
  • the continuous adjustment of the inclination (for example the movement of the finger in the groove) can be ensured in various ways, for example, by means of a pressurized fluid supplied to the finger ball joint by means of a specific circuit.
  • the energy necessary for the adjustment of the inclination can be taken from the energy used for the input shaft.
  • the energy required to adjust the inclination can come from an external source (for example an electric motor).
  • the cylinder block (or barrel) is fixed relative to the crankcase.
  • the energy input to perform the pumping is carried out at the level of the drive shaft only, by the rotation thereof; the number of rotating parts is thus limited.
  • the pump further comprises a return rod.
  • the return rod is arranged between the swash plate and the housing.
  • the return rod is in a ball joint connection with the housing and with the swash plate.
  • the return rod makes it possible to prevent the rotational movement of the swash plate around its axis.
  • the swash plate is driven only by an oscillating movement.
  • the angle of inclination of the turntable relative to the axial direction of the drive shaft is between 70 ° and 90 °.
  • the rotary plate (and a fortiori the swash plate) is inclined at an angle between 0 and 20 ° with respect to a radial direction of the drive shaft.
  • the figures 3 and 4 illustrate, schematically and in a nonlimiting manner, a barrel pump according to one embodiment of the invention.
  • the figure 3 is a three-dimensional view, in which the housing and the compression chambers are not shown.
  • the figure 4 is a kinematic diagram of the pump. In these figures, a single piston 3 is shown. However, the pump according to the invention comprises at least two pistons, these are distributed circumferentially within a cylinder block.
  • the drive shaft 5 is rotatably mounted in a housing 11.
  • the drive shaft 5 is rotated by an external source, not shown, for example a machine. electric and a gearbox.
  • the drive shaft 5 drives the rotary plate 2 by means of a ball joint with finger 8.
  • the position of the ball joint makes it possible to adjust the inclination of the rotary plate 2 relative to the drive shaft 5
  • the rotary plate 2 is linked to a swash plate 7 by a pivot connection along the axis of the rotary plate.
  • the pump 1 further comprises a return rod 9 arranged between the swash plate 7 and the casing 11 by means of ball joints. The return rod 9 prevents the rotation of the swash plate 7 about its axis.
  • the pump 1 comprises a piston 3 driven by a translational movement (back and forth movement) within a compression chamber 4.
  • the compression chamber 4 belongs to the cylinder block (barrel) which is fixed relative to the casing 11.
  • the back and forth movement of the piston 3 is achieved by means of a connecting rod 10 which connects the swash plate 7 and the piston 3 by means of ball joints. This back and forth movement of the piston 3 within the compression chamber 4 makes it possible to pump the fluid.
  • the figure 5 represents, schematically and in a nonlimiting manner, a finger ball joint in three positions according to one embodiment of the invention, in order to illustrate the relative movements between the rotary plate and the drive shaft.
  • the turntable 2 is partially shown: only the central part of the turntable 2 is shown.
  • the finger ball 8 between the drive shaft 5 and the rotary plate 2 is formed by a ball joint between two spherical parts, and by a finger 12 which moves in a groove 13 formed in the rotary plate 2.
  • groove 13 is parallel to the axis of the drive shaft 5.
  • the adjustment of the position of the finger 12 in the groove 13 makes it possible to adjust the angle of inclination of the rotary plate 2 relative to the drive shaft 5.
  • the invention also relates to the use of the pump according to the invention for a drilling operation, in particular for the injection of drilling mud into a wellbore.
  • the pump according to the invention is well suited to this use, due to its flexibility, its compactness, and its resistance to high pressures.
  • the pump according to the invention can be sized to operate up to pressures of the order of 1500 bars, that is to say 150 MPa.
  • the pump according to the invention can be sized to operate at flow rates varying from 30 to 600 m 3 / h.
  • This example relates to a barrel pump according to the invention for which the drive shaft is linked to a prime mover by means of a gearbox with eight ratios.
  • This is a 2,500 HP (approximately 1,900 kW) barrel pump with five pistons.
  • Table 1 shows the rotational speed of the drive shaft as a function of the gearbox ratio: Table 1 Report 1 2 3 4 5 6 7 8 Speed (rpm) 198 269 300 365 407 485 555 660
  • This example shows in particular the impact of the angle of inclination of the plates on the pressure and the flow rate for a barrel pump according to the invention.
  • the figure 6 represents curves of the pressure P (in bars) as a function of the flow rate D (in m 3 / h) for a pump according to the invention for different gearbox ratios (indicated 1st, 2 nd , 3rd, ..., 8th) with a platen inclined 87 ° with respect to the axis of the drive shaft (i.e. with an angle of 3 ° with respect to a radial direction of the drive shaft) .
  • the figure 7 represents curves of the pressure as a function of the flow rate for a pump according to the invention (for the same pump as that used for the figure 6 ) for different gearbox ratios (indicated 1st, 2 nd , 3rd, ..., 8th) with a plate inclined by 70 ° with respect to the drive shaft (i.e. with an angle 20 ° relative to a radial direction of the drive shaft).
  • an angle of inclination of the plates (rotating and oscillating) close to 90 ° allows higher pressures than for an angle of inclination of the plates close to 70 °.
  • an inclination angle of the trays close to 70 ° allows higher flow rates than for an inclination angle of the trays close to 90 ° (thanks to the variable displacement). It is therefore possible to adapt the inclination of the plates according to the desired pumping conditions (pressures, flow rates). It is also noted, thanks to the different ratios of the gearbox, that the speed of rotation of the drive shaft influences the pressure and the flow of the fluid: the pressure is higher at low speed and the flow is higher. at high speed.

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

Description

La présente invention concerne le domaine des pompes, en particulier pour le pompage haute pression, notamment pour des opérations de forage.The present invention relates to the field of pumps, in particular for high pressure pumping, in particular for drilling operations.

De nos jours, les pompes à vilebrequins sont les plus répandues dans l'ensemble des secteurs de l'industrie : les biens d'équipement, les industries pétrolière, gazière et agroalimentaire, le secteur automobile, le bâtiment (chauffage, puits, climatisation, pompes à eau, etc.) et plus spécifiquement pour le traitement de l'eau et des déchets (réseau d'eau et d'assainissement). Néanmoins, elles sont encore construites à partir de concepts datant des années 1930, et ne font l'objet que de très peu d'études de recherche et développement pour améliorer leurs performances, réduire leur coût de revient, minimiser les frais de maintenance ou diminuer leur empreinte environnementale. Ces pompes présentent des limites en termes de puissance, de couple pression / débit (limité par des « coups de bélier » générés par la pression sinusoïdale du vilebrequin), de poids, de rendement et de durée de vie. De plus, elles ne permettent pas d'avoir une cylindrée variable et manquent donc de flexibilité d'utilisation.Nowadays, crankshaft pumps are the most widespread in all sectors of industry: capital goods, the oil, gas and food industries, the automotive sector, construction (heating, wells, air conditioning, water pumps, etc.) and more specifically for the treatment of water and waste (water and sanitation network). However, they are still built from concepts dating from the 1930s, and are the subject of very few research and development studies to improve their performance, reduce their cost price, minimize maintenance costs or reduce their environmental footprint. These pumps have limits in terms of power, pressure / flow torque (limited by "water hammers" generated by the sinusoidal pressure of the crankshaft), weight, efficiency and service life. In addition, they do not allow variable displacement and therefore lack flexibility of use.

En outre, dans le domaine de la production d'hydrocarbures, on observe actuellement que les forages doivent atteindre des profondeurs de plus en plus importantes, ce qui implique de travailler avec des pressions d'injection toujours plus élevées. Les compagnies pétrolières ont donc besoin de pompes (par exemple pour l'injection de boues de forage) à très haute pression pour atteindre les profondeurs requises. Ces dernières doivent également être fiables, économiques, flexibles et compactes, afin de répondre aux demandes toujours plus exigeantes du secteur de l'énergie.In addition, in the field of hydrocarbon production, it is currently observed that boreholes have to reach increasingly great depths, which implies working with ever higher injection pressures. Oil companies therefore need very high pressure pumps (for example for injecting drilling mud) to reach the required depths. These must also be reliable, economical, flexible and compact, in order to meet the ever more demanding demands of the energy sector.

Une autre technologie de pompe volumétrique est la pompe à barillet. Majoritairement destinées au pompage à plus faible pression et débit (elles sont principalement utilisées dans le pompage des huiles hydrauliques), elles offrent de nombreux avantages :

  • Excellent rapport poids / puissance
  • Très bon rapport qualitĂ© / prix
  • Rendements mĂ©caniques et volumĂ©triques intĂ©ressants
  • PossibilitĂ© de cylindrĂ©e variable en rĂ©glant l'inclinaison du plateau
Another positive displacement pump technology is the barrel pump. Mainly intended for pumping at lower pressure and flow (they are mainly used in pumping hydraulic oils), they offer many advantages:
  • Excellent power to weight ratio
  • Very good value for money
  • Interesting mechanical and volumetric performance
  • Possibility of variable displacement by adjusting the inclination of the plate

Les pompes conçues avec un barillet fonctionnent à l'aide d'un système de plateau tournant qui actionne les différents pistons les uns à la suite des autres. Lorsqu'un piston est en phase d'admission, le piston opposé est en mode refoulement, ce qui offre un flux constant en amont et aval de la pompe. La répartition des positions des pistons avec un guidage par le barillet assure une distribution des efforts progressive lors de la rotation de l'arbre entrainé par le moteur.Pumps designed with a barrel operate using a turntable system that actuates the different pistons one after the other. When a piston is in the intake phase, the opposite piston is in the discharge mode, which provides a flow constant upstream and downstream of the pump. The distribution of the positions of the pistons with a guide by the barrel ensures a progressive distribution of the forces during the rotation of the shaft driven by the motor.

Il existe trois grandes architectures de pompe Ă  barillet :

  • Les pompes Ă  barillet fixe (figure 1) : dans cette configuration de pompe 1, oĂą le barillet est fixe, c'est le plateau inclinĂ© 2 qui tourne (entraĂ®nĂ© par l'arbre 5) afin de gĂ©nĂ©rer le mouvement des pistons 3 dans leurs chemises 4. La liaison entre les pistons 3 et le plateau 2 est alors assurĂ© par des patins rotulĂ©s qui frottent sur le plateau 2. L'avantage ici est d'avoir une très faible inertie des pièces en rotation.
  • Les pompes Ă  barillet rotatif (figure 2) : au sein de la pompe 1, c'est le plateau 2 qui est fixe et le barillet 6 portant les pistons 3 est en rotation, assurant ainsi le mouvement des pistons 3 dans leurs chemises 4. La liaison piston 3 - plateau 2 est assurĂ©e de la mĂŞme manière que pour la première configuration. L'avantage de cette architecture est que l'on peut aisĂ©ment rendre le plateau rĂ©glable en inclinaison et ainsi avoir la possibilitĂ© de cylindrĂ©e variable. En revanche, l'inertie des pièces en rotation augmente de façon non nĂ©gligeable puisque le barillet et l'ensemble des pistons sont mis en rotation.
  • Les pompes Ă  barillet avec plateau oscillant : le barillet est fixe dans cette architecture et l'on a deux plateaux, un premier plateau inclinĂ© est en rotation et transfère au second plateau uniquement le mouvement d'oscillation. Ainsi on peut lier les pistons au second plateau oscillant sans la nĂ©cessitĂ© d'Ă©lĂ©ments frottants, par exemple avec une bielle liĂ©e au piston et au plateau par des liaisons rotules. C'est la seule architecture adaptĂ©e au pompage haute pression du fait de l'absence d'Ă©lĂ©ments frottant (on en trouve d'ailleurs quelques-unes sur le marchĂ© de la gĂ©othermie). Elle offre Ă©galement un excellent rendement mĂ©canique.
There are three main barrel pump architectures:
  • Fixed barrel pumps ( figure 1 ): in this configuration of pump 1, where the barrel is fixed, it is the inclined plate 2 which rotates (driven by the shaft 5) in order to generate the movement of the pistons 3 in their liners 4. The connection between the pistons 3 and the plate 2 is then provided by ball-jointed pads which rub against the plate 2. The advantage here is to have a very low inertia of the rotating parts.
  • Rotary barrel pumps ( figure 2 ): within the pump 1, it is the plate 2 which is fixed and the barrel 6 carrying the pistons 3 is in rotation, thus ensuring the movement of the pistons 3 in their liners 4. The piston 3 - plate 2 connection is ensured in the same way as for the first configuration. The advantage of this architecture is that it is easily possible to make the plate tiltable and thus have the possibility of variable displacement. On the other hand, the inertia of the rotating parts increases significantly since the barrel and all of the pistons are rotated.
  • Barrel pumps with oscillating plate: the barrel is fixed in this architecture and there are two plates, a first inclined plate is in rotation and transfers to the second plate only the oscillation movement. Thus, the pistons can be linked to the second swash plate without the need for friction elements, for example with a connecting rod linked to the piston and to the plate by ball joints. It is the only architecture suitable for high pressure pumping due to the absence of friction elements (there are also some on the geothermal market). It also offers excellent mechanical performance.

Des exemples de pompes à barillet avec cylindrée variable, pour lesquels l'inclinaison du plateau rotatif est réglable sont décrits dans les demandes de brevet : US 2014/0186196 , US 6,176,684 , US 5,295,796 . Pour les pompes décrites dans ces demandes de brevet, les systèmes de réglage de l'inclinaison sont soit un servo-piston, soit un système avec moteur électrique et cames, soit un système hydraulique. Ces systèmes sont complexes et ne donnent pas complètement satisfaction.Examples of cylinder pumps with variable displacement, for which the inclination of the rotary plate is adjustable are described in the patent applications: US 2014/0186196 , US 6,176,684 , US 5,295,796 . For the pumps described in these patent applications, the inclination adjustment systems are either a servo-piston, or a system with an electric motor and cams, or a hydraulic system. These systems are complex and are not completely satisfactory.

Pour pallier ces inconvénients, la présente invention concerne une pompe à barillet avec plateau oscillant, pour laquelle l'angle d'inclinaison du plateau rotatif par rapport à l'arbre d'entraînement est réglable au moyen d'une rotule à doigt. Ainsi, l'inclinaison du plateau est réglable de manière continue, ce qui permet une cylindrée variable. De plus, la pompe selon l'invention permet une bonne flexibilité grâce à la variation continue de la cylindrée unitaire, ainsi qu'une bonne fiabilité grâce à la possibilité de mise en fonctionnement progressive de la pompe. En outre la réalisation sous forme d'une pompe à barillet permet une conception compacte de la pompe.To overcome these drawbacks, the present invention relates to a barrel pump with a swash plate, for which the angle of inclination of the rotary plate relative to the drive shaft is adjustable by means of a finger ball joint. Thus, the inclination of the platform is continuously adjustable, which allows a variable displacement. In addition, the pump according to the invention allows good flexibility thanks to the continuous variation of the unit displacement, as well as good reliability thanks to the possibility of progressive start-up of the pump. In addition, the embodiment in the form of a barrel pump allows a compact design of the pump.

Le dispositif selon l'inventionThe device according to the invention

L'invention concerne une pompe Ă  barillet comprenant un carter et comprenant au sein dudit carter :

  • un arbre d'entraĂ®nement,
  • un plateau rotatif entrainĂ© par ledit arbre d'entraĂ®nement,
  • un plateau oscillant entraĂ®nĂ© en oscillation par ledit plateau rotatif, et ledit plateau oscillant Ă©tant en liaison pivot selon l'axe dudit plateau rotatif par rapport audit plateau rotatif,
  • un bloc cylindre comportant au moins deux chambres de compression rĂ©partis circonfĂ©rentiellement, et
  • au moins deux pistons en translation respectivement dans lesdites chambres de compression dudit bloc cylindre, lesdits pistons Ă©tant entraĂ®nĂ©s par ledit plateau oscillant au moyen de bielles,
    Ledit plateau rotatif est entraîné par ledit arbre d'entraînement au moyen d'une rotule à doigt, la position de ladite rotule à doigt déterminant l'inclinaison dudit plateau rotatif et dudit plateau oscillant par rapport audit arbre d'entraînement.
The invention relates to a barrel pump comprising a casing and comprising within said casing:
  • a drive shaft,
  • a rotary plate driven by said drive shaft,
  • a swash plate driven in oscillation by said rotary plate, and said swash plate being in a pivot connection along the axis of said rotary plate relative to said rotary plate,
  • a cylinder block comprising at least two compression chambers distributed circumferentially, and
  • at least two pistons in translation respectively in said compression chambers of said cylinder block, said pistons being driven by said swash plate by means of connecting rods,
    Said rotary table is driven by said drive shaft by means of a finger ball joint, the position of said finger ball joint determining the inclination of said rotary table and said swash plate relative to said drive shaft.

Selon un mode de réalisation de l'invention, la pompe comporte une bielle de rappel, ladite bielle de rappel étant en liaison rotule avec ledit carter et ledit plateau oscillant.According to one embodiment of the invention, the pump comprises a return rod, said return rod being in a ball joint connection with said housing and said swash plate.

Avantageusement, l'angle d'inclinaison dudit plateau rotatif et dudit plateau oscillant par rapport à l'axe dudit arbre d'entraînement est compris entre 70 et 90°.Advantageously, the angle of inclination of said rotary plate and of said swash plate relative to the axis of said drive shaft is between 70 and 90 °.

Conformément à une mise en œuvre, ledit plateau rotatif comporte une gorge dans laquelle se déplace le doigt de ladite rotule à doigt, ladite gorge étant sensiblement parallèle à l'axe dudit arbre d'entrainement.According to one implementation, said rotary plate comprises a groove in which the finger of said ball joint moves, said groove being substantially parallel to the axis of said drive shaft.

Selon une option de réalisation, ladite pompe comporte des moyens de commande de l'inclinaison dudit plateau rotatif par rapport audit arbre d'entraînement.According to one embodiment option, said pump comprises means for controlling the inclination of said rotary plate relative to said drive shaft.

Conformément à une première variante, l'énergie desdits moyens de commande provient d'une source extérieure à ladite pompe, en particulier au moyen d'un fluide sous pression.According to a first variant, the energy of said control means comes from a source external to said pump, in particular by means of a pressurized fluid.

Conformément à une deuxième variante, l'énergie desdits moyens de commande est prélevée sur ledit arbre d'entraînement.According to a second variant, the energy of said control means is taken from said drive shaft.

De manière avantageuse, ledit bloc cylindre est fixe par rapport audit carter.Advantageously, said cylinder block is fixed relative to said housing.

En outre, l'invention concerne une utilisation de ladite pompe à barillet selon l'une des caractéristiques précédentes pour une opération de forage, en particulier pour l'injection de boues de forage dans un puits de forage.In addition, the invention relates to a use of said barrel pump according to one of the preceding characteristics for a drilling operation, in particular for the injection of drilling mud into a wellbore.

Présentation succincte des figuresBrief presentation of figures

D'autres caractéristiques et avantages du dispositif selon l'invention, apparaîtront à la lecture de la description ci-après d'exemples non limitatifs de réalisations, en se référant aux figures annexées et décrites ci-après.

  • La figure 1, dĂ©jĂ  dĂ©crite, illustre une pompe Ă  barillet fixe selon l'art antĂ©rieur.
  • La figure 2, dĂ©jĂ  dĂ©crite, illustre une pompe Ă  barillet rotatif selon l'art antĂ©rieur.
  • La figure 3 illustre une pompe selon un mode de rĂ©alisation de l'invention.
  • La figure 4 illustre schĂ©matiquement une pompe selon un mode de rĂ©alisation de l'invention.
  • La figure 5 illustre une rotule Ă  doigt selon un mode de rĂ©alisation de l'invention dans trois positions.
  • La figure 6 reprĂ©sente des courbes de la pression en fonction du dĂ©bit pour une pompe selon l'invention pour diffĂ©rents rapports de boite de vitesse avec un plateau inclinĂ© de 87° par rapport Ă  l'axe de l'arbre d'entraĂ®nement.
  • La figure 7 reprĂ©sente des courbes de la pression en fonction du dĂ©bit pour une pompe selon l'invention pour diffĂ©rents rapports de boite de vitesse avec un plateau inclinĂ© de 70° par rapport Ă  l'axe de l'arbre d'entraĂ®nement.
Other characteristics and advantages of the device according to the invention will become apparent on reading the following description of non-limiting examples of embodiments, with reference to the appended figures and described below.
  • The figure 1 , already described, illustrates a fixed barrel pump according to the prior art.
  • The figure 2 , already described, illustrates a rotary barrel pump according to the prior art.
  • The figure 3 illustrates a pump according to one embodiment of the invention.
  • The figure 4 schematically illustrates a pump according to one embodiment of the invention.
  • The figure 5 illustrates a finger ball according to one embodiment of the invention in three positions.
  • The figure 6 represents curves of the pressure as a function of the flow rate for a pump according to the invention for different gearbox ratios with a plate inclined by 87 ° relative to the axis of the drive shaft.
  • The figure 7 represents curves of the pressure as a function of the flow rate for a pump according to the invention for different gearbox ratios with a plate inclined by 70 ° relative to the axis of the drive shaft.

Description détaillée de l'inventionDetailed description of the invention

La présente invention concerne une pompe à barillet avec un plateau oscillant. La pompe à barillet a pour but de pomper un fluide (par exemple : eau, huile, gaz, boues de forage, etc.) au moyen d'un déplacement linéaire de plusieurs pistons. Ce type de pompe présente l'avantage d'être compacte, d'avoir des rendements mécaniques et volumétriques intéressants, un excellent rapport poids/puissance. De plus, les pompes à barillet avec un plateau oscillant sont adaptées au pompage haute pression.The present invention relates to a barrel pump with a swash plate. The purpose of the barrel pump is to pump a fluid (for example: water, oil, gas, drilling muds, etc.) by means of a linear displacement of several pistons. This type of pump has the advantage of being compact, of having interesting mechanical and volumetric outputs, an excellent weight / power ratio. In addition, barrel pumps with a swash plate are suitable for high pressure pumping.

La pompe Ă  barillet selon l'invention comporte un carter et comporte au sein d'un carter :

  • un arbre d'entraĂ®nement : celui-ci est entraĂ®nĂ© en rotation, par rapport au carter par une source d'Ă©nergie extĂ©rieure, notamment une machine motrice (par exemple thermique ou Ă©lectrique), en particulier au moyen d'une transmission (par exemple une boĂ®te de vitesses),
  • un plateau rotatif entraĂ®nĂ© par l'arbre d'entraĂ®nement : le plateau rotatif est inclinĂ© par rapport Ă  l'arbre d'entraĂ®nement ; l'inclinaison du plateau rotatif gĂ©nère un mouvement d'oscillation du plateau rotatif ; le plateau rotatif possède un mouvement de rotation et un mouvement d'oscillation par rapport au carter,
  • un plateau oscillant entraĂ®nĂ© en oscillation par le plateau rotatif : le plateau oscillant est en liaison pivot selon l'axe du plateau rotatif par rapport au plateau rotatif ; le plateau rotatif transmet uniquement le mouvement d'oscillation au plateau oscillant et ne transmet pas le mouvement de rotation,
  • un bloc cylindre (appelĂ© barillet), comportant au moins deux chambres de compression (appelĂ©s Ă©galement chemises) rĂ©parties circonfĂ©rentiellement (en d'autres termes les chambres de compression sont rĂ©parties selon un cercle), et
  • au moins deux pistons en translation respectivement dans les chambres de compression, les pistons sont entraĂ®nĂ©s par le plateau oscillant au moyen de bielles (les bielles relient, au moyen de liaisons rotules, le plateau oscillant et les pistons de manière Ă  transformer le mouvement d'oscillation en mouvement de translation des pistons), et la translation des pistons au sein des chambres de compression rĂ©alisent le pompage du fluide.
The barrel pump according to the invention comprises a casing and comprises within a casing:
  • a drive shaft: this is driven in rotation, with respect to the housing by an external energy source, in particular a driving machine (for example thermal or electrical example), in particular by means of a transmission (for example a gearbox),
  • a rotary table driven by the drive shaft: the rotary table is inclined relative to the drive shaft; the inclination of the turntable generates an oscillating movement of the turntable; the turntable has a rotational movement and an oscillating movement relative to the housing,
  • a swash plate driven in oscillation by the turntable: the swash plate is in a pivot connection along the axis of the turntable relative to the turntable; the rotary table only transmits the oscillation movement to the swash plate and does not transmit the rotary movement,
  • a cylinder block (called barrel), comprising at least two compression chambers (also called liners) distributed circumferentially (in other words, the compression chambers are distributed in a circle), and
  • at least two pistons in translation respectively in the compression chambers, the pistons are driven by the swash plate by means of connecting rods (the connecting rods connect, by means of ball joints, the swash plate and the pistons so as to transform the movement of oscillation in translational movement of the pistons), and the translation of the pistons within the compression chambers perform the pumping of the fluid.

Selon l'invention, le plateau rotatif est entraîné par l'arbre d'entraînement au moyen d'une rotule à doigt, la position de la rotule à doigt déterminant l'inclinaison des deux plateaux (rotatif et oscillant) par rapport à l'arbre d'entraînement. On rappelle qu'une liaison rotule à doigt est une liaison entre deux éléments (ici l'arbre d'entraînement et le plateau rotatif), qui dispose de quatre degrés de liaisons et deux degrés de mouvements relatifs ; seulement deux rotations relatives sont possibles, les trois translations et la dernière rotation étant liées. D'une manière générale, il s'agit d'une rotule dotée d'un doigt faisant obstacle à une rotation. Pour l'invention, le doigt de la liaison rotule permet le réglage de l'inclinaison des plateaux par rapport à l'arbre d'entraînement. En effet, la pompe comprend des moyens pour commander la rotule à doigt, et donc l'inclinaison des plateaux par rapport à l'arbre d'entraînement.According to the invention, the rotary plate is driven by the drive shaft by means of a finger ball joint, the position of the finger ball joint determining the inclination of the two plates (rotary and oscillating) with respect to the drive shaft. It will be recalled that a ball joint with a finger is a connection between two elements (here the drive shaft and the rotary plate), which has four degrees of connection and two degrees of relative movement; only two relative rotations are possible, the three translations and the last rotation being linked. Generally speaking, it is a ball joint with a finger preventing rotation. For the invention, the finger of the ball joint makes it possible to adjust the inclination of the plates relative to the drive shaft. In fact, the pump comprises means for controlling the finger ball joint, and therefore the inclination of the plates relative to the drive shaft.

Ainsi, l'inclinaison des plateaux rotatif et oscillant est réglable de manière continue, ce qui permet une cylindrée variable. En effet, l'inclinaison des plateaux influe sur la course des pistons. De plus, la pompe selon l'invention permet une bonne flexibilité grâce à la variation continue de la cylindrée unitaire. En outre, la pompe selon l'invention permet une bonne fiabilité grâce à la possibilité de mise en fonctionnement progressive de la pompe : par exemple, lors du démarrage, l'angle d'inclinaison peut être faible, et par la suite, il peut être augmenté en fonction des conditions souhaitées (débit et pression du fluide). Cette fiabilité ne peut pas être obtenue avec une pompe dont l'inclinaison des plateaux est fixe, ou pour laquelle l'inclinaison ne peut pas varier de manière continue.Thus, the inclination of the rotating and oscillating plates is continuously adjustable, which allows variable displacement. Indeed, the inclination of the plates influences the stroke of the pistons. In addition, the pump according to the invention allows good flexibility thanks to the continuous variation of the unit displacement. In addition, the pump according to the invention allows good reliability thanks to the possibility of gradually starting the pump: for example, during start-up, the angle of inclination may be small, and subsequently, it may be increased according to the desired conditions (flow rate and pressure of the fluid). This reliability cannot be obtained with a pump whose inclination of the plates is fixed, or for which the inclination cannot vary continuously.

Les plateaux peuvent avoir sensiblement la forme de disque. Toutefois, les plateaux peuvent avoir n'importe quelle forme. Seules les chambres de compression (et les pistons) sont réparties sur un cercle.The trays may have substantially the shape of a disc. However, the trays can have any shape. Only the compression chambers (and the pistons) are distributed in a circle.

Avantageusement, la pompe selon l'invention peut comporter un nombre de pistons compris entre trois et quinze, de préférence entre cinq et onze. Ainsi, un nombre élevé de pistons offre un flux continu en amont et en aval de la pompe.Advantageously, the pump according to the invention can include a number of pistons between three and fifteen, preferably between five and eleven. Thus, a high number of pistons provides a continuous flow upstream and downstream of the pump.

Ainsi grâce à ce système, le mouvement de rotation en entrée (arbre d'entraînement) est transformé dans un premier temps en mouvement d'oscillation (plateau oscillant) et dans un deuxième temps dans un mouvement de translation, c'est-à-dire un mouvement de va et vient (pistons). Le mouvement de va et vient des pistons dans les chambres de compression assure le pompage du fluide.Thus, thanks to this system, the input rotational movement (drive shaft) is first transformed into an oscillating movement (swash plate) and secondly into a translational movement, i.e. say a back and forth movement (pistons). The reciprocating movement of the pistons in the compression chambers ensures the pumping of the fluid.

De manière classique, la pompe comporte en outre une entrée et une sortie du fluide à pomper. Le fluide passe par l'entrée de la pompe, entre dans une chambre de compression, est comprimé, puis refoulé de la pompe par la sortie au moyen du piston.Conventionally, the pump further comprises an inlet and an outlet for the fluid to be pumped. The fluid passes through the inlet of the pump, enters a compression chamber, is compressed, and then discharged from the pump through the outlet by means of the piston.

De plus, classiquement, les liaisons pivots sont formées par des paliers ou des roulements, favorisant le mouvement relatif des éléments.In addition, conventionally, the pivot connections are formed by bearings or bearings, promoting the relative movement of the elements.

Selon un mode de réalisation de l'invention, le réglage de l'inclinaison peut se faire en déplaçant le doigt de la rotule dans une gorge réalisée dans le plateau rotatif, l'axe de la gorge pouvant être parallèle à celui de l'axe de rotation de l'arbre d'entraînement.According to one embodiment of the invention, the inclination can be adjusted by moving the finger of the ball joint in a groove made in the rotary plate, the axis of the groove being able to be parallel to that of the axis rotation of the drive shaft.

Conformément à une mise en oeuvre de l'invention, le réglage continu de l'inclinaison (par exemple le déplacement du doigt dans la gorge) peut être assuré de différentes manières, par exemple, au moyen d'un fluide sous pression acheminé à la rotule à doigt au moyen d'un circuit spécifique.According to one implementation of the invention, the continuous adjustment of the inclination (for example the movement of the finger in the groove) can be ensured in various ways, for example, by means of a pressurized fluid supplied to the finger ball joint by means of a specific circuit.

Selon une conception de l'invention, l'énergie nécessaire au réglage de l'inclinaison (par exemple le déplacement du doigt dans la gorge) peut être prélevée de l'énergie utilisée pour l'arbre d'entrée. Alternativement, l'énergie nécessaire au réglage de l'inclinaison peut provenir d'une source externe (par exemple un moteur électrique).According to one design of the invention, the energy necessary for the adjustment of the inclination (for example the movement of the finger in the groove) can be taken from the energy used for the input shaft. Alternatively, the energy required to adjust the inclination can come from an external source (for example an electric motor).

De préférence, le bloc cylindre (ou barillet) est fixe par rapport au carter. Ainsi, l'apport d'énergie pour réaliser le pompage est réalisé au niveau de l'arbre d'entraînement uniquement, par la rotation de celui-ci ; le nombre de pièces en rotation est ainsi restreint.Preferably, the cylinder block (or barrel) is fixed relative to the crankcase. Thus, the energy input to perform the pumping is carried out at the level of the drive shaft only, by the rotation thereof; the number of rotating parts is thus limited.

Conformément à une option de réalisation de l'invention, la pompe comporte en outre une bielle de rappel. La bielle de rappel est disposée entre le plateau oscillant et le carter. La bielle de rappel est en liaison rotule avec le carter et avec le plateau oscillant. La bielle de rappel permet d'empêcher le mouvement de rotation du plateau oscillant autour de son axe. Ainsi, le plateau oscillant est animé uniquement d'un mouvement d'oscillation.In accordance with one embodiment of the invention, the pump further comprises a return rod. The return rod is arranged between the swash plate and the housing. The return rod is in a ball joint connection with the housing and with the swash plate. The return rod makes it possible to prevent the rotational movement of the swash plate around its axis. Thus, the swash plate is driven only by an oscillating movement.

Le plateau oscillant n'ayant pas de mouvement de rotation, aucun élément frottant ne peut être interposé entre le plateau oscillant et les bielles transmettant le mouvement aux pistons.As the swash plate has no rotational movement, no friction element can be interposed between the swash plate and the connecting rods transmitting the movement to the pistons.

Selon un mode de réalisation de l'invention, l'angle d'inclinaison du plateau rotatif par rapport à la direction axiale de l'arbre d'entraînement est compris entre 70° et 90°. En d'autres termes, le plateau rotatif (et a fortiori le plateau oscillant) est incliné d'un angle compris entre 0 et 20° par rapport à une direction radiale de l'arbre d'entraînement.According to one embodiment of the invention, the angle of inclination of the turntable relative to the axial direction of the drive shaft is between 70 ° and 90 °. In other words, the rotary plate (and a fortiori the swash plate) is inclined at an angle between 0 and 20 ° with respect to a radial direction of the drive shaft.

Les figures 3 et 4 illustrent, schématiquement et de manière non limitative, une pompe à barillet selon un mode de réalisation de l'invention. La figure 3 est une vue tridimensionnelle, dans laquelle le carter et les chambres de compression ne sont pas représentés. La figure 4 est un schéma cinématique de la pompe. Sur ces figures, un seul piston 3 est représenté. Toutefois, la pompe selon l'invention comporte au moins deux pistons, ceux-ci sont répartis circonférentiellement au sein d'un bloc cylindre.The figures 3 and 4 illustrate, schematically and in a nonlimiting manner, a barrel pump according to one embodiment of the invention. The figure 3 is a three-dimensional view, in which the housing and the compression chambers are not shown. The figure 4 is a kinematic diagram of the pump. In these figures, a single piston 3 is shown. However, the pump according to the invention comprises at least two pistons, these are distributed circumferentially within a cylinder block.

Pour la pompe 1 selon le mode de réalisation illustré, l'arbre d'entraînement 5 est monté en rotation dans un carter 11. La rotation de l'arbre d'entraînement 5 est réalisée par une source extérieure non représentée, par exemple une machine électrique et une boîte de vitesses. L'arbre d'entraînement 5 entraîne le plateau rotatif 2 au moyen d'une liaison rotule à doigt 8. La position de la rotule à doigt permet de régler l'inclinaison du plateau rotatif 2 par rapport à l'arbre d'entraînement 5. Le plateau rotatif 2 est lié à un plateau oscillant 7 par une liaison pivot selon l'axe du plateau rotatif. La pompe 1 comporte en outre une bielle de rappel 9 disposée entre le plateau oscillant 7 et le carter 11 au moyen de liaisons rotules. La bielle de rappel 9 empêche la rotation du plateau oscillant 7 autour de son axe. La pompe 1 comporte un piston 3 animé d'un mouvement de translation (mouvement de va et vient) au sein d'une chambre de compression 4. La chambre de compression 4 appartient au bloc cylindre (barillet) fixe par rapport au carter 11. Le mouvement de va et vient du piston 3 est réalisé au moyen d'une bielle 10 qui relie le plateau oscillant 7 et le piston 3 au moyen de liaisons rotules. Ce mouvement de va et vient du piston 3 au sein de la chambre de compression 4 permet de pomper le fluide.For the pump 1 according to the illustrated embodiment, the drive shaft 5 is rotatably mounted in a housing 11. The drive shaft 5 is rotated by an external source, not shown, for example a machine. electric and a gearbox. The drive shaft 5 drives the rotary plate 2 by means of a ball joint with finger 8. The position of the ball joint makes it possible to adjust the inclination of the rotary plate 2 relative to the drive shaft 5 The rotary plate 2 is linked to a swash plate 7 by a pivot connection along the axis of the rotary plate. The pump 1 further comprises a return rod 9 arranged between the swash plate 7 and the casing 11 by means of ball joints. The return rod 9 prevents the rotation of the swash plate 7 about its axis. The pump 1 comprises a piston 3 driven by a translational movement (back and forth movement) within a compression chamber 4. The compression chamber 4 belongs to the cylinder block (barrel) which is fixed relative to the casing 11. The back and forth movement of the piston 3 is achieved by means of a connecting rod 10 which connects the swash plate 7 and the piston 3 by means of ball joints. This back and forth movement of the piston 3 within the compression chamber 4 makes it possible to pump the fluid.

La figure 5 représente, schématiquement et de manière non limitative, une rotule à doigt dans trois positions selon un mode de réalisation de l'invention, afin d'illustrer les mouvements relatifs entre le plateau rotatif et l'arbre d'entraînement. Sur cette figure, le plateau rotatif 2 est représenté de manière partielle : seule la partie centrale du plateau rotatif 2 est illustrée. La rotule à doigt 8 entre l'arbre d'entraînement 5 et le plateau rotatif 2 est formée d'une liaison rotule entre deux parties sphériques, et par un doigt 12 qui se déplace dans une gorge 13 formée dans le plateau rotatif 2. La gorge 13 est parallèle à l'axe de l'arbre d'entraînement 5. Ainsi, seules deux rotations entre le plateau rotatif 2 et l'arbre d'entraînement sont autorisées. On remarque que le réglage de la position du doigt 12 dans la gorge 13 permet de régler l'angle d'inclinaison du plateau rotatif 2 par rapport à l'arbre d'entraînement 5.The figure 5 represents, schematically and in a nonlimiting manner, a finger ball joint in three positions according to one embodiment of the invention, in order to illustrate the relative movements between the rotary plate and the drive shaft. In this figure, the turntable 2 is partially shown: only the central part of the turntable 2 is shown. The finger ball 8 between the drive shaft 5 and the rotary plate 2 is formed by a ball joint between two spherical parts, and by a finger 12 which moves in a groove 13 formed in the rotary plate 2. groove 13 is parallel to the axis of the drive shaft 5. Thus, only two rotations between the rotary plate 2 and the drive shaft are allowed. Note that the adjustment of the position of the finger 12 in the groove 13 makes it possible to adjust the angle of inclination of the rotary plate 2 relative to the drive shaft 5.

L'invention concerne également l'utilisation de la pompe selon l'invention pour une opération de forage, en particulier pour l'injection de boues de forage dans un puits de forage. En effet, la pompe selon l'invention est bien adaptée à cette utilisation, par sa flexibilité, sa compacité, et sa résistance aux hautes pressions.The invention also relates to the use of the pump according to the invention for a drilling operation, in particular for the injection of drilling mud into a wellbore. In fact, the pump according to the invention is well suited to this use, due to its flexibility, its compactness, and its resistance to high pressures.

Par exemple la pompe selon l'invention peut être dimensionnée pour fonctionner jusqu'à des pressions de l'ordre de 1500 bars, c'est-à-dire 150 MPa. En outre, la pompe selon l'invention peut être dimensionnée pour fonctionner à des débits variant de 30 à 600 m3/h.For example, the pump according to the invention can be sized to operate up to pressures of the order of 1500 bars, that is to say 150 MPa. In addition, the pump according to the invention can be sized to operate at flow rates varying from 30 to 600 m 3 / h.

ExempleExample

Les caractéristiques et avantages du système selon l'invention apparaîtront plus clairement à la lecture de l'exemple d'application ci-après.The characteristics and advantages of the system according to the invention will emerge more clearly on reading the application example below.

Cet exemple concerne une pompe à barillet selon l'invention pour lequel l'arbre d'entraînement est lié à une machine motrice au moyen d'une boîte de vitesse avec huit rapports. Il s'agit d'une pompe à barillet de 2500 HP (environ 1900 kW) comportant cinq pistons. Le tableau 1 indique la vitesse de rotation de l'arbre d'entraînement en fonction du rapport de la boîte de vitesses : Tableau 1 Rapport 1 2 3 4 5 6 7 8 Vitesse (tr/min) 198 269 300 365 407 485 555 660 This example relates to a barrel pump according to the invention for which the drive shaft is linked to a prime mover by means of a gearbox with eight ratios. This is a 2,500 HP (approximately 1,900 kW) barrel pump with five pistons. Table 1 shows the rotational speed of the drive shaft as a function of the gearbox ratio: Table 1 Report 1 2 3 4 5 6 7 8 Speed (rpm) 198 269 300 365 407 485 555 660

Au travers de cet exemple, on montre notamment l'impact de l'angle d'inclinaison des plateaux sur la pression et le débit pour une pompe à barillet selon l'invention.This example shows in particular the impact of the angle of inclination of the plates on the pressure and the flow rate for a barrel pump according to the invention.

La figure 6 représente des courbes de la pression P (en bars) en fonction du débit D (en m3/h) pour une pompe selon l'invention pour différents rapports de boite de vitesse (indiqués 1st, 2nd, 3rd, ..., 8th) avec un plateau incliné de 87° par rapport à l'axe de l'arbre d'entraînement (c'est-à-dire avec un angle de 3° par rapport à une direction radiale de l'arbre d'entraînement).The figure 6 represents curves of the pressure P (in bars) as a function of the flow rate D (in m 3 / h) for a pump according to the invention for different gearbox ratios (indicated 1st, 2 nd , 3rd, ..., 8th) with a platen inclined 87 ° with respect to the axis of the drive shaft (i.e. with an angle of 3 ° with respect to a radial direction of the drive shaft) .

La figure 7 représente des courbes de la pression en fonction du débit pour une pompe selon l'invention (pour la même pompe que celle utilisée pour la figure 6) pour différents rapports de boite de vitesse (indiqués 1st, 2nd, 3rd, ..., 8th) avec un plateau incliné de 70° par rapport à l'arbre d'entraînement (c'est-à-dire avec un angle de 20° par rapport à une direction radiale de l'arbre d'entraînement).The figure 7 represents curves of the pressure as a function of the flow rate for a pump according to the invention (for the same pump as that used for the figure 6 ) for different gearbox ratios (indicated 1st, 2 nd , 3rd, ..., 8th) with a plate inclined by 70 ° with respect to the drive shaft (i.e. with an angle 20 ° relative to a radial direction of the drive shaft).

On remarque qu'un angle d'inclinaison des plateaux (rotatif et oscillant) proche de 90° permet des pressions plus élevées que pour un angle d'inclinaison des plateaux proche de 70°. De plus, un angle d'inclinaison des plateaux proche de 70° permet des débits plus élevés que pour un angle d'inclinaison des plateaux proche de 90° (grâce à la cylindrée variable). Il est donc possible d'adapter l'inclinaison des plateaux en fonction des conditions de pompage souhaitées (pressions, débits). On constate également, grâce aux différents rapports de la boîte de vitesse, que la vitesse de rotation de l'arbre d'entraînement influe sur la pression et le débit du fluide : la pression est plus élevée à faible vitesse et le débit est plus élevé à vitesse élevée.Note that an angle of inclination of the plates (rotating and oscillating) close to 90 ° allows higher pressures than for an angle of inclination of the plates close to 70 °. In addition, an inclination angle of the trays close to 70 ° allows higher flow rates than for an inclination angle of the trays close to 90 ° (thanks to the variable displacement). It is therefore possible to adapt the inclination of the plates according to the desired pumping conditions (pressures, flow rates). It is also noted, thanks to the different ratios of the gearbox, that the speed of rotation of the drive shaft influences the pressure and the flow of the fluid: the pressure is higher at low speed and the flow is higher. at high speed.

Claims (9)

  1. Cylinder/plate pump comprising a housing (11) and comprising within said housing (11):
    - a drive shaft (5),
    - a rotary plate (2) driven by said drive shaft (5),
    - a wobble plate (7) made to wobble by said rotary plate (2), said wobble plate (7) being connected so as to pivot about the axis of said rotary plate (2) relative to said rotary plate (2),
    - a cylinder block having at least two circumferentially distributed compression chambers (4), and
    - at least two pistons (3) that are respectively able to move in translation in said compression chambers (4) of said cylinder block, said pistons (3) being driven by said wobble plate (7) by means of rods (10),
    characterized in that said rotary plate (2) is driven by said drive shaft (5) by means of a pegged ball joint (8), the position of said pegged ball joint (8) determining the inclination of said rotary plate (2) and of said wobble plate (7) relative to said drive shaft (5).
  2. Pump according to Claim 1, wherein the pump has a return rod (9), said return rod (9) being connected to said housing (11) and said wobble plate (7) by a ball-joint connection.
  3. Pump according to either of the preceding claims, wherein the angle of inclination of said rotary plate (2) and of said wobble plate (7) relative to the axis of said drive shaft (5) is between 70 and 90°.
  4. Pump according to one of the preceding claims, wherein said rotary plate (2) has a groove (13) in which the peg (12) of said pegged ball joint (8) moves, said groove (13) being substantially parallel to the axis of said drive shaft (5).
  5. Pump according to one of the preceding claims, wherein said pump (1) has means for controlling the inclination of said rotary plate relative to said drive shaft (5).
  6. Pump according to Claim 5, wherein the energy for said control means comes from a source that is external to said pump (1), in particular by means of a pressurized fluid.
  7. Pump according to Claim 5, wherein the energy for said control means is drawn from said drive shaft (5) .
  8. Pump according to one of the preceding claims, wherein said cylinder block is fixed relative to said housing (11).
  9. Use of said cylinder/plate pump (1) according to one of the preceding claims for a drilling operation, in particular for injecting drilling mud into a drilled well.
EP18700369.4A 2017-01-25 2018-01-16 Wobble pump comprising a wobble plate Active EP3574214B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1750584A FR3062178B1 (en) 2017-01-25 2017-01-25 BARREL PUMP WITH OSCILLATING PLATE
PCT/EP2018/051013 WO2018137974A1 (en) 2017-01-25 2018-01-16 Wobble pump comprising a wobble plate

Publications (2)

Publication Number Publication Date
EP3574214A1 EP3574214A1 (en) 2019-12-04
EP3574214B1 true EP3574214B1 (en) 2020-11-25

Family

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Application Number Title Priority Date Filing Date
EP18700369.4A Active EP3574214B1 (en) 2017-01-25 2018-01-16 Wobble pump comprising a wobble plate

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US (1) US10900337B2 (en)
EP (1) EP3574214B1 (en)
CN (1) CN110226036B (en)
CA (1) CA3049492A1 (en)
FR (1) FR3062178B1 (en)
WO (1) WO2018137974A1 (en)

Families Citing this family (1)

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Publication number Priority date Publication date Assignee Title
CN114576125B (en) * 2022-03-23 2024-07-09 č‹‘äşšĺż  Deflection cylinder pump

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1303796A (en) * 1962-10-01 1962-09-14 Adjustable variable flow piston rotary pump
US3712758A (en) * 1970-09-10 1973-01-23 Int Harvester Co Variable displacement pump
US4037993A (en) * 1976-04-23 1977-07-26 Borg-Warner Corporation Control system for variable displacement compressor
US4235116A (en) * 1978-05-10 1980-11-25 U.S. Philips Corporation Balanced variable wobble plate drive
DE3324587A1 (en) * 1982-07-10 1984-01-19 NL Sperry-Sun, Inc., Stafford, Tex. DRILL HOLE TRANSMITTER FOR A SLUDGE PULSE TELEMETRY SYSTEM
JPH05126029A (en) 1991-10-31 1993-05-21 Toyota Autom Loom Works Ltd Variable capacity piston pump
US5979294A (en) * 1996-02-08 1999-11-09 Whitemoss, Inc. Method and apparatus for controlling axial pump
JP3234506B2 (en) * 1996-09-09 2001-12-04 株式会社日立製作所 Fuel pump
US6361286B1 (en) * 1996-09-09 2002-03-26 Hitachi, Ltd Fuel pump
US6176684B1 (en) 1998-11-30 2001-01-23 Caterpillar Inc. Variable displacement hydraulic piston unit with electrically operated variable displacement control and timing control
US20030206811A1 (en) * 2002-05-06 2003-11-06 Hypro Corporation Variable displacement positive displacement pump
US7794212B2 (en) * 2004-07-10 2010-09-14 Hugelman Rodney D Multi-piston pump/compressor
US7047867B2 (en) * 2004-07-27 2006-05-23 Ford Global Technologies, Llc Oscillating device for adjusting the displacement of a fluid pump
WO2007104257A1 (en) * 2006-03-14 2007-09-20 Zhu Raphael An axial plunger pump or motor
US20110197752A1 (en) * 2008-10-29 2011-08-18 Rodney Dale Hugelman Axial piston multi circuit machine
JP4934749B1 (en) * 2011-02-23 2012-05-16 株式会社小松製作所 Variable displacement hydraulic pump / motor
JP6401509B2 (en) * 2014-06-12 2018-10-10 Ｋｙｂ株式会社 Piston pump and piston pump valve plate
CN204591607U (en) * 2015-04-01 2015-08-26 浙江工业大学 Two-dimensional cylindrical guide rail axial piston pump
US20190112926A1 (en) * 2017-10-16 2019-04-18 Curaegis Technologies, Inc. Rotatable piston assembly

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
US20190360473A1 (en) 2019-11-28
CA3049492A1 (en) 2018-08-02
FR3062178A1 (en) 2018-07-27
EP3574214A1 (en) 2019-12-04
FR3062178B1 (en) 2019-06-07
CN110226036A (en) 2019-09-10
WO2018137974A1 (en) 2018-08-02
US10900337B2 (en) 2021-01-26
CN110226036B (en) 2021-08-31

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