Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
  • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
  • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
  • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
  • F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2/00—Rotary-piston machines or pumps
  • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
  • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
  • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
  • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2/00—Rotary-piston machines or pumps
  • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
  • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
  • F04C2/084—Toothed wheels
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2240/00—Components
  • F04C2240/20—Rotors
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2240/00—Components
  • F04C2240/30—Casings or housings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
  • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle

Definitions

• the invention relates to gear pumps for liquid or compressible fluid.
• It relates more particularly to a new pump structure design, aimed at achieving better pumping performance.
• the invention finds, moreover, an advantageous application to be implemented in volumetric pumps, even if it can be applied to other types of pumps.
• Synchronous gear pumps have two gears each provided with peripheral teeth. In such pumps, the teeth of the two gears do not touch. However, the teeth of the two gears can nest together. Each of the two gears is rotated by a shaft. In other words, such pumps comprise two drive shafts in rotation of the gears. A housing for synchronizing the rotation of the shafts is then provided in a sealed portion of the pump.
• the sprocket teeth for synchronous gear pumps have a shape that allows the rotation of the two sprockets.
• the face of the teeth which is oriented towards the direction of rotation of the pinion is called “front face”.
• the other side of the teeth is called "back face”.
• the self-driven gear pumps also have two gears each provided with peripheral teeth, uniformly distributed.
• one of the pinions first pinion
• This first pinion drives the second pinion in rotation, by contact of the nested teeth in each other.
• the teeth then have, for this purpose, a shape such that it allows the rotation of the two gears.
• the front face of the teeth is then called “active face”. This is the tooth face of a first pinion which comes into contact with the face of a tooth of the other pinion, and which allows the rotation drive of the other pinion.
• the other face of the tooth that is to say the rear face, is also called “inactive face”.
• the invention is concerned with self-driven pinion pumps.
• pinions with lobe-shaped peripheral teeth are found in synchronized gear pumps.
• lobes will include larger teeth whose end may have a curved shape.
• the radial projections of the gear wheels are called “teeth” when they are smaller, narrower than the lobes, with one end more pointed or with sharp edges.
• US 2014/0271313 discloses a positive displacement pump interleaving a three-lobe pinion with a three-toothed pinion. Because of the differences in shape and size of the lobes and the intertwined teeth, it is necessary for each shaft to have several stages of lobed and / or toothed gears angularly offset from one another so that when a first lobe and tooth pinion gear is no longer driven, a second set of lobe and tooth pinions take over.
• Such an embodiment does not give satisfactory pumping results, particularly because of the necessary relay between the different stages of lobe and toothed gears and because of liquid leaks (or fluid) from one stage to another during pumping, except to implement between the pumping stages of the radial fins preventing the fluid from leaking.
• the invention aims to offer a more efficient solution to those described in documents FR 2 399 559 and US 2014/0271313.
• a gear pump comprising a pumping chamber in which a first shaft and a second shaft are rotated about their respective axes, each of the first and second shafts carrying at least one hydraulic pumping element ensuring the hydraulically pumping a fluid into the pumping chamber, said at least one hydraulic pumping element of each of said first and second shafts being positioned in said pumping chamber and each having at least a first radial projection.
• each of said first and second shafts also carries at least one mechanical drive gear in rotation of each of said first and second shafts, each pinion of mechanical drive having radial second projections.
• said at least one mechanical drive gear is distinct from said at least one hydraulic pumping element.
• said at least one first radial projection and said second radial projections are in different numbers.
• the pump according to the invention distinguishes, in the pumping chamber, the elements ensuring the hydraulic drive of the fluid from those ensuring the mechanical drive in rotation of the shafts.
• the elements ensuring the hydraulic drive of the fluid are no longer used also to ensure the mechanical drive of the rotating shafts about their axis. It is thus possible to provide hydraulic drive elements with very different profiles, depending on the characteristics of the fluid to be pumped, and even profiles that would not be retained today by those skilled in the art because these profiles would not allow the mechanical self-drive of trees.
• the pinions dedicated to the mechanical drive of the shafts may have a disk shape, since they no longer have to extend substantially over the entire length of the shaft. tree in the pumping chamber.
• Such pinions can thus be made of stronger materials, ensuring a longer life of the pump and better self-drive shafts rotating about their axis.
• the invention may also include the following features, taken separately or in combination:
• said at least one hydraulic pumping element of each shaft is formed by at least one lobe wheel, the lobes constituting first projections for the hydraulic pumping element,
• said at least one first projection has a first radial height, in that the second projections have a second height; radial, and in that said first radial height is larger than said second radial height,
• each of the first and second shafts carries a mechanical drive pinion positioned between two hydraulic pumping members, each of the first and second shafts carries a hydraulic pumping member positioned between two mechanical drive gears, each of the first and second shafts carries a hydraulic pumping element and a mechanical drive pinion,
• said at least one mechanical drive gear is attached to said at least one hydraulic pumping element
• the pump comprises means for angular adjustment of the position of said at least one hydraulic pumping element with respect to said at least one mechanical drive gear about the axis of said first and second shafts,
• said at least one hydraulic pumping element and said at least one mechanical drive pinion are made of different materials
• said at least one hydraulic pumping element and said at least one mechanical drive gear of each shaft are made in one piece.
• FIG. 1 is a perspective view of a gear pump according to the invention, showing a partially open pumping chamber in order to show the elements it encloses;
• FIG. 2 is an exploded perspective view of various elements internal to the pumping chamber of the pump shown in FIG. 1
• FIG. 3 is a front view of two shafts of the pump shown in FIG. 1, on which are mounted two mechanical drive gears and two hydraulic pumping elements
• FIG. 4 is a perspective view of a shaft on which is mounted a hydraulic pumping element and a drive gear
• FIG. 5 is a front view of a mechanical drive pinion of the gear pump shown. in FIGS. 1 to 4, FIG.
• FIG. 6 is a front view of internal elements of a pump according to the invention, according to an alternative embodiment, this view illustrating two mechanical drive gears and two different hydraulic pumping elements. of those shown in FIGS. 1 to 4,
• FIG. 7 is a front view of two mechanical drive gears and two hydraulic pumping elements different from those illustrated in FIG. 6,
• FIG. 8 is a perspective view of internal elements of a pump according to the invention, according to yet another variant embodiment,
• FIG. 9 is a perspective view of internal elements of a pump according to the invention, according to yet another variant embodiment,
• Figure 10 is a perspective view of a gear pump according to the invention, showing a partially open pumping chamber to show the elements it encloses, the pump being different from that illustrated in Figure 1 in particular.
• FIG. 1 shows a positive displacement pump 1 according to the invention, comprising a pumping chamber 2.
• the pumping chamber 2 has an internal cavity 3 whose cross section is substantially elliptical.
• the chamber has, transversely, an inlet opening 4 of a fluid, through which a pumped fluid is introduced into the cavity 3 of the chamber 2, and an outlet opening 5 through which the pumped fluid is expelled.
• the chamber 2 also has, longitudinally, two end walls 6 and 7, closing the cavity 3.
• the positive displacement pump 1 is a self-driven gear pump.
• one of the shafts exits the cavity of the chamber 1 to be connected to a rotating drive system (not shown).
• the other shaft (the shaft 8 in this case) is mounted crazy in the cavity of the chamber.
• the ends 12 of the shaft 8 are inserted into cylindrical housings 10 and 11 which are integral with the end walls 6 and 7, respectively, the cylindrical housings 10 and 11 being open towards the cavity 3.
• the end of the shaft 9 which is not connected to a rotary drive motor is also inserted into a cylindrical housing 13 integral with one of the end walls of the chamber 2.
• the ends of the shafts 8 and 9 positioned in the cylindrical housings 10, 11 and 13 are free to rotate about their axis in the cylindrical housings 10, 11 and 13.
• each of the shafts 8 and 9 carries a mechanical drive gear 14 (see in particular the figure 2) the two mechanical drive gears 14 having projections 15 uniformly distributed around a disk 16, the projections of the two mechanical drive gears 14 being intertwined with each other when the two shafts are positioned in the pump.
• the two gears 14 thus constitute a gear for the pump 1.
• the projections 15 of the mechanical drive gears 14 are teeth in the sense of the present description, because these projections are small (compared to the size of other radial projections which will be presented later) and each have a free end 17 substantially shaped tip.
• the protrusions 15 all have, moreover, an axial symmetry on either side of the rays R of the disk 16 following each of which they extend (see Figure 5 in particular).
• This symmetry allows a rotational drive of the mechanical drive pinion 14 in one direction or the other around its axis. Therefore, the shaft 9 can be rotated about its axis D9 in one direction or the other.
• the direction of rotation of the shaft 9 is determined according to whether it is desired to introduce the pump fluid into an opening 4 or into another 5 in the pumping chamber 2.
• All the mechanical drive gears 14 shown in the exemplary embodiments each have fifteen projections 15 (or teeth 15), and the projections 15 have a height H.
• the disc 16 of the mechanical drive pinion 1 4 has a central through opening 1 8 whose diameter substantially corresponds to that of the shaft 8 (or the shaft 9), and is preferably slightly greater than that of the shaft 8 (or shaft 9), in order to thread the pinion on the shaft 8 (or on the shaft 9).
• the radial thickness E of the disc 1 6, taken between the opening 1 8 and the outer wall 1 9 of the disc 1 6 between two teeth 1 5 is greater than the height H of the teeth 1 5 of the mechanical drive gears 14.
• the radius P of each of the mechanical drive gears 14 corresponds to the addition of the radius of the opening 1 8, the thickness E of the disc 1 6 and the height H of a tooth 1 5.
• each shaft 8 and 9 also carries a hydraulic pumping element, placed with a mechanical drive pinion 14 in the pumping chamber 2.
• Figures 1 to 4 show a first example of hydraulic pumping elements.
• the hydraulic pumping elements are made by lobed wheels 21, visible in particular in FIG. 2.
• Each of the lobed wheels 21 extends in an axial direction along a length L1 which is greater than the length L2 on which the mechanical drive gear 14 extends.
• the addition of the lengths L1 and L2 substantially corresponds to the length L3 of the cavity 3 of the chamber, taken substantially between the two end internal walls 6 and 7 of the pumping chamber 2 (see FIGS. 1 and 4 in particular) .
• Each of the lobed wheels 21 has a central axial through opening 22 of cylindrical shape, whose diameter corresponds substantially to that of the shaft 8 (or of the shaft 9), and is preferably slightly greater than that of the shaft 8 (or shaft 9), in order to thread the pinion on the shaft 8 (or on the shaft 9).
• Each of the wheels 20 has, between the central opening 22 and the lobes 21, a central portion 23 whose radial thickness E1, taken between the opening 22 and the outer wall 24 of the wheel 20 between two lobes 21, is smaller at the height H1 of the lobes 21 of the wheels 20.
• the radius P1 of each of the lobed wheels 20 corresponds to the addition of the radius of the opening 22, the thickness E1 of the central portion 23 and the height H1 of a lobe 21.
• radius P1 of the lobe wheels 20 is greater than the radius P of the mechanical drive gears 14.
• the radial thickness E1 of the lobe wheels 20 is smaller than the radial thickness E of the mechanical drive gears 14.
• the height H1 of the lobes is greater than the height of the projections 15 (or teeth 15) of the mechanical drive gears 14.
• the mechanical gear gears 14 and the lobed wheels 20 may be made of different materials.
• the advantage of producing in two parts the element 20 dedicated to hydraulic pumping and the pinion 14 dedicated to the mechanical drive is that the pinion 14 can be made of materials that are more resistant (or more adapted to the characteristics of the fluid to be produced. pumping) than conventional drive sprockets (which are also dedicated to hydraulic pumping, in contrast to the invention).
• each of the mechanical drive gears 14 is traversed by openings 31, the openings 31 being formed in a direction parallel to the axis of the gears 14 and through the central disk 16 ( Figure 2).
• three through openings 31 are provided in the central disc 16 of the mechanical drive gears 14 and three threaded blind holes in the lobed wheels 21.
• the three through openings 31 and the three blind holes are made at equal distances from each other about the axis of the pinion 14 or the wheel 20, respectively.
• the angle between two blind holes or two through openings is therefore substantially Fixing is performed by screwing through the opening 31 into the blind hole of each lobed wheel 21.
• These adjustment means comprise blind holes in the wheels 20 (mentioned above), screws 30 (shown in FIG. 8 for example), and through openings 32 with a particular profile 32, formed through the drive pinion. mechanical 14, which will now be presented with reference to FIG.
• Three openings 32 pass through the disk 16 in a direction parallel to the axis of the mechanical gear pinion 14.
• the three openings 32 are arranged at equal distances from each other, around the axis of the mechanical gear pinion 14.
• the three openings 32 each have a bean shape, extending along an arc of a circle around the axis of the mechanical drive pinion 14, thus having an oblong shape.
• This oblong shape of the openings 32, curved, allows a rotation of the mechanical drive gear 14 around the shaft 8 or 9 relative to the lobe wheel 20, after partial screwing of the screws in the blind holes of the wheels 20, so that the position of a tooth 15 can be varied with respect to the position of a lobe 21 by varying the position of the screw in the opening 32 of an end 33 of the opening to the other end 34.
• the adjustment angle is more or less important.
• the gear wheels 14 and the lobed wheels 20 do not have the same diameter, when one or more teeth 15 are placed between two lobes 21 (FIG. 3 for example), the teeth 15 and a portion of the disc 16 form a wall 28 laterally closing at least partially a space 29 between two lobes 21.
• This wall 28 acts as a deflector on the fluid which is pumped into the pumping chamber 2, channeling on either side of the wall 28 the fluid between two lobes 21 during the rotation of the lobe wheels 21.
• This offset leads to better performance by increasing the frequency of the pump pulsations. For example, in the case of a six lobe wheel 21 shown in FIGS. 1 to 4, the normal pulse frequency is 6. With an appropriate angular positioning of the teeth 15 of the mechanical gear pinion 14 with respect to lobes 21 of the wheel 20, it is possible to obtain a frequency of 12.
• the shape of the lobes 21 of the lobe wheel 20 can be arbitrary, since it has no not to be used also for the mechanical drive of the shafts 8 and 9 on which they are mounted.
• the lobes 21 of a wheel 20 positioned on a shaft (8) do not bear on the lobes 21 of a second wheel 20 positioned on the other shaft (9).
• the shape of the lobes can therefore be more easily adapted to the consistency of the fluid to be pumped.
• FIGS. 1 to 4 shows lobed wheels 21 whose lobes 21 have asymmetrical profiles (unlike the teeth of the mechanical drive gears 14).
• the lobes 21 each have a top portion 25, a substantially convex front portion 26 and a substantially flat rear portion 27.
• the invention thus makes it possible to use conventional lobe wheels 21 in the pump chamber 2 of the pump according to the invention, which is economical.
• hydraulic pumping elements could have yet different shapes without departing from the scope of the invention.
• FIG. 6 shows the two shafts 8 and 9 on which are mounted two mechanical drive gears 14 and two impeller wheels 35.
• the blades 35 are of rectangular section and shape and they are positioned radially uniformly around a cylinder 36.
• blade wheels 35 are inexpensive to manufacture.
• FIG. 7 Another embodiment is further shown in FIG. 7: in this example, the two mechanical drive gears 14 are each fixed to a three-lobe wheel 40, on each of the shafts 8 and 9.
• the three lobes 40 of the wheels 20 are identical and uniformly distributed around the axis of each of the wheels 20.
• the lobes 40 each have a wide base 41 which extends over substantially one third of the periphery of the wheel 20.
• Such an embodiment ensures a better hydraulic pumping of the fluid in the pumping chamber 2.
• the fluid is less sheared in the pumping chamber so that such lobe wheels can be implemented in a pump to pump a pump. fluid supporting little to be mixed if one wishes to keep its consistency.
• FIG. 8 shows yet another embodiment, implementing hydraulic pumping elements consisting of cylindrical wheels 20, on each of which teeth 50 extend in a helical movement: each tooth extends from a first end 51 of the cylinder of the wheel 20 at a second end 52 at a helix angle.
• the teeth 50 are larger than the teeth 15 of the mechanical gear gears 14.
• the teeth 50 have a top 53 on either side of which two symmetrical and convex lateral portions 54 and 55 extend.
• Each of the wheels 20 has fifteen teeth 50.
• This embodiment has a certain advantage if it is desired to suppress the pulsations in the pumping chamber 2.
• This embodiment allows any helix angle without imposing a minimum length to achieve the hydraulic pumping element.
• the invention is not limited to the implementation of a particular hydraulic pumping element and that a positive displacement pump could further comprise other hydraulic pumping elements without departing from the scope of the invention.
• the hydraulic pumping elements could consist of worm positioned at the ends of the shafts 8 and 9 without departing from the scope of the invention.
• the invention also extends to pumps that may comprise several stages of gear gears 14 and / or hydraulic pumping elements 20.
• FIG. 9 shows two shafts 8 and 9 (the same as those of the pumps described above) on each of which is mounted a lobed wheel 21 such as that shown in FIGS. 1 to 4, on both sides. other of which are mounted two mechanical drive gears 14.
• the two mechanical drive gears 14 are each fixed on an end face 60 of the lobed wheel 21, in the same manner as that previously described in the context of the mounting of the mechanical drive pinion 14 on the wheel 20 1 to 4.
• each of the end faces 60 is provided with blind holes in which a screw 30 can be screwed.
• FIG. 9 is of interest in the context of the production of a volumetric pump having a particularly long chamber: the presence of two mechanical drive gears 14 at both ends of the pumping chamber 2 makes it possible to balance driving the shafts 8 and 9 in rotation about their respective axes. This also allows a good distribution of the fluid in the pumping chamber 2.
• FIG. 10 shows yet another embodiment: the pumping chamber 2 encloses two lobed wheels 20, between which is positioned a mechanical drive pinion 14.
• the wheels 20 may be indexed angularly relative to each other by means of a fitting on a spline shaft.
• the mechanical drive is positioned at the center of the chamber: by angularly adjusting the position of the lobes 21 relative to the position of the teeth 15 of the pinion 14, two stages 70 and 71 are created. hydraulic pumping, which increases the performance of the pump as explained above.
• the mechanical drive pinion 14 also serves as a screen between the two lobe wheels 20, which makes it possible to limit fluid leaks in the pumping chamber of a stage 70 lobes 21 to the other 71.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Rotary Pumps (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)

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Applications Claiming Priority (2)

Publications (2)

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• 2015
  • 2015-03-11 FR FR1552016A patent/FR3033601B1/fr active Active
• 2016
  • 2016-02-17 US US15/554,096 patent/US10197057B2/en active Active
  • 2016-02-17 BR BR112017017847-8A patent/BR112017017847B1/pt active IP Right Grant
  • 2016-02-17 PT PT167079300T patent/PT3268610T/pt unknown
  • 2016-02-17 PL PL16707930T patent/PL3268610T3/pl unknown
  • 2016-02-17 EP EP16707930.0A patent/EP3268610B1/de active Active
  • 2016-02-17 MX MX2017011592A patent/MX2017011592A/es unknown
  • 2016-02-17 WO PCT/FR2016/050359 patent/WO2016142597A1/fr active Application Filing
  • 2016-02-17 ES ES16707930T patent/ES2770104T3/es active Active
• 2017
  • 2017-09-22 ZA ZA2017/06425A patent/ZA201706425B/en unknown

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