WO2015097637A1 - Pompe à déplacement variable pour fluides à régulation modulée, et procédé de régulation de son déplacement - Google Patents

Pompe à déplacement variable pour fluides à régulation modulée, et procédé de régulation de son déplacement Download PDF

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Publication number
WO2015097637A1
WO2015097637A1 PCT/IB2014/067211 IB2014067211W WO2015097637A1 WO 2015097637 A1 WO2015097637 A1 WO 2015097637A1 IB 2014067211 W IB2014067211 W IB 2014067211W WO 2015097637 A1 WO2015097637 A1 WO 2015097637A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
pressure
stage
spring
displacement
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.)
Ceased
Application number
PCT/IB2014/067211
Other languages
English (en)
Inventor
Leonardo Cadeddu
Matteo Calderoni
Joao Paulo VIVIURKA
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
VHIT SpA
Original Assignee
VHIT SpA
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from IT001063A external-priority patent/ITTO20131063A1/it
Priority claimed from IT001072A external-priority patent/ITTO20131072A1/it
Application filed by VHIT SpA filed Critical VHIT SpA
Priority to EP14830721.8A priority Critical patent/EP3087275B1/fr
Publication of WO2015097637A1 publication Critical patent/WO2015097637A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis

Definitions

  • the present invention relates to variable displacement pumps, and more particularly it concerns a pump of this kind with modulated regulation and a method of regulating its displacement.
  • the invention is applied in a pump for the lubrication oil of the engine and/or the drive system of a motor vehicle, and particular reference will be made to such a preferred application in the description below.
  • WO 2013/140304 discloses a positive displacement rotary pump with variable displacement in which the regulation exploits the variation of the relative position between an external regulation ring and the rotor eccentrically rotating within the same ring.
  • the variation is obtained through a rotation of the ring.
  • the latter is configured as a multistage rotary piston directly driven by the pressure of the pumped fluid, where at least one stage is permanently exposed to the action of the fluid and at least another stage intervenes, in addition to the first stage, upon command of an electrically controlled valve with on-off operation.
  • the spring rotation is opposed by a spring guided on a tappet coupled with the ring by means of a spherical joint.
  • the on-off actuation of the second stage does not ensure regulation stability, and the provision of the guide tappet and of its articulation on the ring gives rise to frictions causing hysteresis in the pump reaction.
  • modulation members are connected between the second stage and the driving members and are arranged to modulate a regulation pressure acting on the second stage depending on a control signal supplied by the driving members and on the pressure conditions.
  • the modulating members include a distributor arranged to: take, depending on the control signal, at least a first and a second extreme configuration in correspondence of the maximum displacement and the minimum displacement of the pump, respectively; expose the second stage to the same pressure conditions as those acting on the first stage in the first extreme configuration, and to atmospheric pressure conditions in the second extreme configuration; and modulate the pressure acting on the second stage when the pressure of the pumped fluid reaches, while increasing or decreasing, respectively, a threshold pressure set for the intervention of members opposing a movement of a movable element of the distributor.
  • the invention also concerns a method of regulating the displacement of a variable displacement pump for fluids, wherein movable regulation members are provided, which include at least a pair of actuation stages, of which a first stage is permanently exposed to the pressure conditions of the pumped fluid and is arranged to make the regulation members move against the action of opposing members, and a second stage is arranged to act concordantly with the opposing members in a manner controlled by external control members, and wherein a step of making the regulation members move comprises the step of modulating the driving pressure to which the second stage is exposed depending on the control signal and the pressure conditions of the pumped fluid.
  • FIG. 1 is a front view of a pump according to the invention, without the cover, in the maximum displacement position;
  • Fig. 2 is a view similar to Fig. 1, showing the pump in the minimum displacement position
  • FIGS. 3 and 4 are simplified diagrams showing the opposing force and its arm in the maximum and minimum displacement conditions
  • a pump 1 of the above kind comprises a body (schematised by dotted-and-dashed line 10), having a cavity within which regulation ring 11 (hereinafter also referred to simply as stator) is mounted so as to be freely rotatable along an arc of circumference about an axis 18 internal to the stator itself.
  • Stator 11 has a chamber 12 accommodating rotor 13, keyed on a shaft 14 parallel to the rotation axis of stator 11. In the Figures, it is assumed that the rotor rotates in counterclockwise direction.
  • stator 11 causes a variation of the relative eccentricity between stator 11 and rotor 13, and hence a variation of the displacement, between a condition of maximum eccentricity and displacement (Fig. 1), which is taken also in rest conditions of the pump, and a condition of minimum eccentricity and displacement (Fig. 2).
  • a chamber 15 balancing the radial thrusts exerted on stator 11 because of the hydraulic pressure acting on the arc of the wall of chamber 12 corresponding to the balancing chamber.
  • Balancing chamber 15 is defined by gaskets 16, 17 and it communicates with the devices utilising the pumped fluid, in particular with the lubrication circuit of the engine or the drive system of a motor vehicle.
  • Stator 11 is configured as a multistage rotary piston for displacement regulation, directly driven by pressurised fluid coming for instance from the devices utilising the pumped fluid (for instance, from a point of the lubrication circuit located downstream the oil filter).
  • the rotary piston has a pair of actuation stages (or surfaces) formed by portions 19, 20 of the external surface of stator 1 1. Said stages are exposed to the action of the pressurised fluid introduced into chambers 21, 22, where portions of the stator surface adjacent to actuation surfaces 19, 20 move in fluid-tight manner.
  • Reference numerals 33, 34 denote ducts through which the regulation pressures act on stages 19, 20. Possible further stages can be formed in lightening chambers formed in stator 11, as disclosed in WO 2013/140304.
  • stages 19, 20 are formed so that the pressure applied to stage 19 generates a force Fl in turn arranged to generate a torque causing stator rotation towards the minimum displacement position against the action of an opposing member 23 (in particular a helical spring), and so that the pressure applied to stage 20 generates a force F2 generating an antagonistic torque concordant with the torque generated by a force F3 due to the reaction of spring 23.
  • an opposing member 23 in particular a helical spring
  • the torques generated by Fl, F2, F3 will also be referred to hereinafter as torque 1, torque 2 and torque 3.
  • Spring 23 is preloaded so as to prevent the rotation of stator 11 - and hence to keep it in the position shown in Fig. 1 - as long as the resultant of the pressures applied to stages 19, 20 is lower than a predetermined threshold, and to subsequently keep the pump displacement at the value corresponding to the pressure threshold. Such a condition is attained when an equilibrium is established between torques 1, 2 and 3.
  • Spring 23 has a longitudinal axis 28 (Figs. 3, 4) which does not cross rotation axis 18 of stator 11, and is located in a seat 24 formed in body 10. Its end loops 23 A, 23B, suitably arranged close to one another and preferably tapered, abut against flat end surface 24 A of seat 24 and on a flat portion 25 of the external surface of stator 11, respectively.
  • Planes 24A, 25 have formed thereon centring projections 26, 27 engaging end loops
  • projections 23 A, 23B of spring 23 Such projections are aimed at maintaining end loops 23 A, 23B univocally positioned and at preventing the spring from "sliding" over planes 24 A, 25 because of the radial and/or axial components of the applied forces, should the friction coefficients of the materials of spring 23, body 10 and stator 11 allow such a sliding.
  • recesses surrounding loops 23 A, 23B might be provided, or a projection might be provided on one side and a recess on the other side.
  • the projections or the recesses may even have non-circular shape.
  • planes 24A, 25 are formed so that they are mutually parallel when the displacement is minimum, and so that they define a certain angle under all other conditions, said angle being maximum in the maximum displacement condition.
  • Spring 23 will have therefore a minimum (substantially zero) deformation and a substantially rectilinear axis in the minimum displacement condition, and will attain the maximum deformation in the maximum displacement condition.
  • the behaviour of the spring axis can be defined by a polynomial of third degree.
  • centring elements 26, 27 are the only elements retaining spring 23 and that, since they cooperate only with the end loops, they have no guiding function. The remaining portion of the spring therefore can freely deform itself during the rotation of stator 11.
  • force vector F3 applied to plane 25 at the centre of element 27 creates a non-linear counter-motive torque since, as clearly shown in Figs. 3 and 4, the force and its application arm b3 (distance from rotation axis 18 of stator 11) change as stator 11 is rotates.
  • force F3 is the resultant of the components of the whole of the radial and tangential forces acting on plane 25 and has smaller intensity and arm than in the minimum displacement condition (Fig. 4), where the vector is perpendicular to plane 25.
  • the diameter of the wire cooperates to the definition of such a ratio.
  • the characteristics of spring 23 will depend on the pump displacement, on the difference between the maximum and the minimum displacement, on the regulating pressure, and, in case of a rotary pump, on the driving geometry of rotor 13.
  • chamber 21 is directly supplied with pressurised oil through a branch 33A of outlet duct 33 of oil filter 32, whereas chamber 22 is supplied through a spool valve 40 modulating the displacement regulation pressure, said valve communicating with chamber 22 through a duct 34.
  • spool 41 In spool valve 40, spool 41, movable against the action of an opposing spring 46, defines a first annular chamber 42, it too connected to duct 33 (branch 33B), and a second annular chamber 43, where duct 33 ends and which communicates, depending on the position of spool 41, either with the first annular chamber 42 or a third annular chamber 44. The latter in turn may communicate with a non-pressurised portion of circuit 30, in particular with oil sump 35.
  • a fourth annular chamber 45 is also supplied with pressurised oil from duct 33 (branch 33C).
  • Spool 41 further has a first end portion 41A onto which spring 46 is guided, whereas the opposite end portion 4 IB slides in fluid-tight manner within a further chamber 47.
  • spool 41 may be positioned so as to let pressurised oil from branch 33D of duct 33 (Fig. 2) pass into chamber 47, or to intercept such oil, making chamber 47 discharge towards oil sump 35
  • the pressurised oil arrives also to chamber 22 in the pump through branch 33B of duct 33, chambers 42, 43 of valve 30 communicating with each other and duct 34, and, by acting on surface 20, generates, due to force F2, the antagonistic torque (torque 2) concordant with torque 3.
  • the pressures in both chambers 21, 22 are equivalent and the direction of action of resultant Fl - F2 will depend on the difference between the areas of surfaces 19, 20. In the illustrated example, taking into account that surface 19 has a greater area than surface 20, Fl > F2 and resultant Fl - F2 will act in counterclockwise direction.
  • pressurised oil is supplied to chamber 45 of valve 40 thereby applying, onto an annular surface 41C of spool 41 defining such a chamber, a force opposing the force generated by spring 46.
  • spool 41 begins moving to the left, thereby progressively shutting communication between chambers 42, 43 and progressively establishing communication between chambers 43, 44, and hence with oil sump 35, until a condition of equilibrium between the forces acting on the spool itself and the reaction of spring 46 is attained.
  • a certain reduction in the pressure applied to stage 20, and hence of torque 2 takes place.
  • stator 11 When the oil pressure is such that torque 1 - torque 2 > torque 3, stator 11 will rotate counterclockwise thereby reducing its eccentricity relative to rotor 13, and consequently the pump displacement.
  • maximum regulated pressure value Such a pressure value, referred to as “maximum regulated pressure value", will be substantially maintained even as the rotation speed of the pump and the permeability of the engine (intended as the amount of oil used by the engine) vary.
  • valve 50 When a suitable command arrives from the electronic control unit (not shown) of the vehicle, electrically-controlled valve 50 passes to the position shown in Fig. 2, where it supplies chamber 47 with pressurised oil. When the force due to the joint pressure of the oil introduced into chambers 45 and 47 exceeds the force exerted by spring 46, it causes spool 41 to move completely to the left, whereby pump chamber 22 discharges oil to sump 35 through chambers 43, 44 of valve 40 and thus passes to atmospheric pressure. Torque 2 becomes therefore 0 and the only torque opposing torque 3 is torque 1. Such a condition is referred to as "minimum regulated pressure value". Also in this case spool 41 will take an equilibrium position depending on the oil pressure conditions in duct 33 and on the reaction force of spring 46.
  • the invention actually attains the desired aims. Thanks to the provision of the torque generated by F2, that adds to the torque generated by force F3 due to opposing spring 23, the force exerted by the latter to keep the equilibrium pressure can actually be reduced and, in the minimum pressure condition, actuation will be due only to the pressure applied to the first stage 19. Moreover, modulating the pressure applied to the second stage 20 by means of spool valve 40 makes actuation simple and stable. Lastly, the provision of non- guided opposing spring 23 reduces friction and hysteresis between the two directions of displacement regulation.
  • electrically-controlled valve 50 is an on-off valve
  • a proportional electrically-controlled valve could however be used for modulating the decrease and/or the increase of the driving pressure supplied by spool valve 40 (an hence the decrease or the increase of the pressure in chamber 22), thereby allowing a possible electronic management resulting from the engine "mapping".
  • the invention can be applied also to pumps where the rotation of the stator is indirectly driven by said pressure, or to pumps where the displacement regulation movement is different from the stator rotation illustrated here (so-called "pendulum” pumps, pumps with a rocking or oscillating stator, pumps with a stator translation, and so on).
  • pendulum pumps with a rocking or oscillating stator
  • the invention can be applied also to pumps with a rotor of different kind, e.g. a gear rotor (for instance G-rotor or split G-rotor) or to non-rotary pumps, for instance pumps with pistons operated by a rotating plate with variable inclination.

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

Abstract

Pompe à déplacement variable (1) comprenant une bague de régulation (11) possédant au moins une paire d'étages d'actionnement (19, 20), le premier étage étant exposé en permanence à des conditions de pression du fluide pompé et étant conçu pour entraîner le déplacement de la bague de régulation (11) à l'encontre de l'action d'un ressort (23), et le second étage étant conçu pour agir en accord avec le ressort (23) d'une manière commandée par un clapet à commande électrique (50). Un clapet à boisseau (40), commandé par le clapet à commande électrique (50) et les conditions de pression du fluide pompé, est relié entre le second étage (20) et le clapet à commande électrique (50) et est conçu pour moduler une pression de régulation agissant sur le second étage (20) en fonction d'un signal de commande envoyé par le clapet à commande électrique (50) et de telles conditions de pression. L'invention se rapporte également à un procédé de régulation du déplacement d'une telle pompe.
PCT/IB2014/067211 2013-12-23 2014-12-22 Pompe à déplacement variable pour fluides à régulation modulée, et procédé de régulation de son déplacement Ceased WO2015097637A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14830721.8A EP3087275B1 (fr) 2013-12-23 2014-12-22 Pompe à déplacement variable pour fluides à régulation modulée, et procédé de régulation de son déplacement

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
IT001063A ITTO20131063A1 (it) 2013-12-23 2013-12-23 Pompa a cilindrata regolabile per fluidi con modulazione della regolazione, e metodo per la regolazione della sua cilindrata
ITTO2013A001063 2013-12-23
IT001072A ITTO20131072A1 (it) 2013-12-24 2013-12-24 Pompa a cilindrata regolabile e metodo per la regolazione della cilindrata di tale pompa
ITTO2013A001072 2013-12-24

Publications (1)

Publication Number Publication Date
WO2015097637A1 true WO2015097637A1 (fr) 2015-07-02

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Family Applications (2)

Application Number Title Priority Date Filing Date
PCT/IB2014/067217 Ceased WO2015097639A1 (fr) 2013-12-23 2014-12-22 Pompe à cylindrée variable et procédé pour réguler la cylindrée de la pompe
PCT/IB2014/067211 Ceased WO2015097637A1 (fr) 2013-12-23 2014-12-22 Pompe à déplacement variable pour fluides à régulation modulée, et procédé de régulation de son déplacement

Family Applications Before (1)

Application Number Title Priority Date Filing Date
PCT/IB2014/067217 Ceased WO2015097639A1 (fr) 2013-12-23 2014-12-22 Pompe à cylindrée variable et procédé pour réguler la cylindrée de la pompe

Country Status (2)

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EP (2) EP3087275B1 (fr)
WO (2) WO2015097639A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150260186A1 (en) * 2014-03-14 2015-09-17 Hitachi Automotive Systems Steering, Ltd. Variable displacement vane pump
CN105351188A (zh) * 2015-11-04 2016-02-24 湖南机油泵股份有限公司 一种组合阀式二级变排量叶片泵控制系统
DE102015117433A1 (de) * 2015-10-13 2017-04-13 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe
WO2018051905A1 (fr) * 2016-09-16 2018-03-22 Ｋｙｂ株式会社 Pompe à palettes à débit variable
JP2018044535A (ja) * 2016-09-16 2018-03-22 Ｋｙｂ株式会社 可変容量型ベーンポンプ
EP3524816A4 (fr) * 2017-10-27 2020-06-03 Hunan Oil Pump Co., Ltd. Pompe à huile à cylindrée variable de niveau 3 ou de niveau 4 à base de soupape électromagnétique à commutateur double

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012149929A2 (fr) * 2011-05-05 2012-11-08 Ixetic Bad Homburg Gmbh Pompe à cylindrée variable
WO2013140304A1 (fr) 2012-03-19 2013-09-26 Vhit Spa Pompe rotative à cylindrée variable et procédé de commande de la cylindrée

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US2669189A (en) * 1947-09-05 1954-02-16 Houdaille Hershey Corp Adjustable fluid pump
DE3001673C2 (de) * 1980-01-18 1984-06-28 Audi Nsu Auto Union Ag, 7107 Neckarsulm Regelbare Flügelzellenpumpe
DE102005033293A1 (de) * 2005-07-16 2007-01-25 Zf Lenksysteme Gmbh Verdrängerpumpe mit variablem Fördervolumen
AT502189B1 (de) * 2005-07-29 2007-02-15 Miba Sinter Holding Gmbh & Co Flügelzellenpumpe
US7959171B2 (en) 2007-11-26 2011-06-14 Nissan Motor Co., Ltd. Lower spring seat mounting structure for vehicle suspension
DE102010022677B4 (de) * 2010-06-04 2016-06-30 Nidec Gpm Gmbh Flügelzellenpumpe
DE102010055141A1 (de) 2010-12-18 2012-08-02 Audi Ag Federunterlage für eine freistehende Tragfeder eines Kraftfahrzeugs

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012149929A2 (fr) * 2011-05-05 2012-11-08 Ixetic Bad Homburg Gmbh Pompe à cylindrée variable
WO2013140304A1 (fr) 2012-03-19 2013-09-26 Vhit Spa Pompe rotative à cylindrée variable et procédé de commande de la cylindrée

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150260186A1 (en) * 2014-03-14 2015-09-17 Hitachi Automotive Systems Steering, Ltd. Variable displacement vane pump
US9903366B2 (en) * 2014-03-14 2018-02-27 Hitachi Automotive Systems Steering, Ltd. Variable displacement vane pump
DE102015117433A1 (de) * 2015-10-13 2017-04-13 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe
DE102015117433B4 (de) 2015-10-13 2019-01-03 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe
CN105351188A (zh) * 2015-11-04 2016-02-24 湖南机油泵股份有限公司 一种组合阀式二级变排量叶片泵控制系统
WO2018051905A1 (fr) * 2016-09-16 2018-03-22 Ｋｙｂ株式会社 Pompe à palettes à débit variable
JP2018044535A (ja) * 2016-09-16 2018-03-22 Ｋｙｂ株式会社 可変容量型ベーンポンプ
WO2018051904A1 (fr) * 2016-09-16 2018-03-22 Ｋｙｂ株式会社 Pompe à palettes à capacité variable
CN109715949A (zh) * 2016-09-16 2019-05-03 Ｋｙｂ株式会社 可变容量型叶片泵
EP3524816A4 (fr) * 2017-10-27 2020-06-03 Hunan Oil Pump Co., Ltd. Pompe à huile à cylindrée variable de niveau 3 ou de niveau 4 à base de soupape électromagnétique à commutateur double

Also Published As

Publication number Publication date
EP3087276A1 (fr) 2016-11-02
EP3087275A1 (fr) 2016-11-02
EP3087276B1 (fr) 2020-03-11
WO2015097639A1 (fr) 2015-07-02
EP3087275B1 (fr) 2022-08-03

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