EP3049671B1 - Bague d'étanchéité pour distributeur de pompe hydraulique - Google Patents

Bague d'étanchéité pour distributeur de pompe hydraulique Download PDF

Info

Publication number
EP3049671B1
EP3049671B1 EP14796176.7A EP14796176A EP3049671B1 EP 3049671 B1 EP3049671 B1 EP 3049671B1 EP 14796176 A EP14796176 A EP 14796176A EP 3049671 B1 EP3049671 B1 EP 3049671B1
Authority
EP
European Patent Office
Prior art keywords
ring
sealing
face
stator
hydraulic pump
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
EP14796176.7A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3049671A1 (fr
Inventor
Vianney Rabhi
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.)
Individual
Original Assignee
Individual
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
Application filed by Individual filed Critical Individual
Publication of EP3049671A1 publication Critical patent/EP3049671A1/fr
Application granted granted Critical
Publication of EP3049671B1 publication Critical patent/EP3049671B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/047—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the outer ends of the cylinders
    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0465—Distribution members, e.g. valves plate-like
    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
    • F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks
    • 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
    • F04B1/20—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 rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate
    • 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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/303—Control of machines or pumps with rotary cylinder blocks by turning the valve plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/11—Kind or type liquid, i.e. incompressible
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the present invention relates to a sealing ring for a hydraulic pump distributor.
  • a hydraulic mechanism for motor or pump consisting of a cylinder block having a surface of communication with the outside, a plurality of cylinders, which are formed in the cylinder block and within each of which slides a piston.
  • the hydraulic mechanism comprises a distribution window provided with orifices corresponding to ramps of corrugations while the cylinder block is provided with feed or exhaust ports of the cylinders.
  • the hydraulic mechanism comprises at least two separate operating cylinders.
  • Axial or radial piston pumps with rotating cylinders and particularly those with variable displacement are most often constituted by a rotor in which hydraulic cylinders are arranged. In each of said cylinders, a hydraulic piston moves back and forth.
  • Said rotor usually has a feed face maintained in contact with the most tight possible with a distribution face - also called ice or distribution plate - arranged on the surface of a stator, the latter may be part of a pump body.
  • the supply face generally comprises orifices each connected to one of the hydraulic cylinders, while the distribution face comprises at least a suction lumen through which the hydraulic pistons can draw hydraulic fluid, and at least one discharge lumen through which said pistons can discharge said fluid, said orifices and said lumens constituting a hydraulic distributor.
  • said orifices are alternately connected to a suction duct by the suction lumen, then with a discharge duct by the discharge lumen. It follows from this that a flow of hydraulic fluid can be established between said ducts following the movements back and forth that the hydraulic pistons, each in its hydraulic cylinder.
  • hydraulic fluid leaks inevitably occur between the supply face and the distribution face. As a result, part of the hydraulic fluid passes directly from the discharge pipe to the suction pipe or vice versa, while another part of the fluid passes directly from said pipes to an inner casing. which generally comprise said hydraulic pumps on the other hand. These leaks reduce the volumetric and energy efficiency of said pumps.
  • said platen may for example be an inclined plate or a plateau of rods.
  • the distributor is most often constituted by a distribution face positioned on the outer surface of a first cylinder integral with the stator, while the supply face is positioned on the inner surface of a second cylinder, which caps the first cylinder, and which is secured to the rotor.
  • the seal between said faces is preferably obtained from a low clearance left between the first and the second cylinder, the manufacture of the latter requiring high machining precision.
  • sealing ring for a hydraulic pump distributor has a low cost, its manufacture does not involve any process complex or expensive material.
  • Said ring is also designed to offer great strength and long life and can operate in the field of high hydraulic pressures.
  • Said ring is also applicable to any hydraulic pump or hydraulic motor-pump with fixed or variable displacement, that said pump or motor-pump is in particular pallet, axial piston, radial piston, rotary cylinder or not and whatever the liquid, gaseous, or semi-liquid fluid that it operates.
  • the sealing ring for hydraulic pump distributor comprises a ring groove which comprises a ring bearing face on its sides which are oriented perpendicularly to the low-pressure sealing surface on the stator side, said face of the ring. support cooperating with a shoulder support ring that includes the continuous seal ring.
  • the sealing ring for a hydraulic pump distributor comprises a ring groove which has a ring sealing face on its sides which are oriented perpendicularly to the low-pressure sealing surface on the stator side, said face of the ring. sealing cooperating with a ring sealing shoulder that includes the continuous sealing ring.
  • the sealing ring for a hydraulic pump distributor comprises a ring seal lifter which is a flexible metal blade integral with the ring sealing shoulder.
  • the sealing ring for a hydraulic pump distributor comprises a ring sealing lip which is positioned on, below or in the extension of the ring sealing shoulder.
  • the sealing ring for a hydraulic pump distributor comprises a ring sealing lip which is constituted by a lateral seal made of flexible material held simultaneously in contact with the ring groove and with the face of the ring. stator side ring.
  • the sealing ring for a hydraulic pump distributor comprises a compression-decompression seal which has at least one sectoral compression-decompression chamber which defines a closed and sealed volume with the stator-side face of the ring and the bottom and / or the axial or radial sides of the ring groove.
  • the sealing ring for a hydraulic pump distributor comprises a compression-decompression seal which comprises a cellular stiffening structure in which is arranged the compression-decompression sector cell, said honeycomb structure being made in a rigid material that can be directly or indirectly held in position relative to the continuous sealing ring by the rotational stop means, while said rigid material may in all or in part be coated with a flexible material that can enter into contact with the stator side of the ring face on the one hand, and / or with the bottom and / or the axial or radial sides of the ring groove on the other hand.
  • the sealing ring for a hydraulic pump distributor comprises a honeycomb stiffening structure which is integrated with the stator-side face of the ring and which is made in the same piece of material as the continuous sealing ring.
  • the sealing ring for a hydraulic pump distributor comprises a compression-decompression track which has at least one compression-decompression vector orifice through which a compression-decompression sector duct opens, which connects with the ring face.
  • rotor side the closed and sealed volume defined by the compression-decompression sector cell, said sector orifice being positioned in such a way that the supply orifice is facing said sector orifice once per revolution of the pump rotor, said orifice sectorial then connecting the supply duct to said sealed volume via the sectoral duct compression-decompression.
  • the hydraulic pump distributor sealing ring according to the present invention comprises a side seal and a compression-decompression seal which form a single piece.
  • the hydraulic pump distributor sealing ring according to the present invention comprises a ring sealing face which is positioned approximately perpendicular to the circumferential contact line.
  • the hydraulic pump distributor sealing ring according to the present invention comprises a ring sealing face which is positioned approximately vertically above the circumferential contact line while the ring bearing face is further away from the bottom of the ring. the ring groove and the dispensing recess that said sealing face so that it is offset relative to the plumb line of the circumferential contact line.
  • the hydraulic pump distributor sealing ring comprises at least one of the axial faces of the ring groove which is formed by the axial face of a ring mounting ring which encloses the pump stator.
  • the hydraulic pump distributor sealing ring comprises a pump stator distribution face and a pump rotor supply face which are cylindrical while at least one of the intake-discharge ports cooperates with at least one radial force compensating light arranged in the pump stator, the latter light emerging from the pump stator distribution face and facing the pump rotor supply face, said compensation light being further located - in said stator - diametrically opposite the intake-discharge lumen with which it cooperates and being connected by a radial force compensation duct to the inlet-discharge duct to which said light is connected. intake-discharge with which it cooperates.
  • the sealing ring for a hydraulic pump distributor comprises a compensation light which opens out from the pump stator distribution face via a radial force compensation groove in which is housed at low axial play and / or tangential radial force compensation sealing plate.
  • the sealing ring for hydraulic pump distributor comprises a radial force compensation sealing plate which is traversed right through its thickness by a compensating recess which connects the conduit. radial force compensation with the pump rotor supply face,
  • the sealing ring for a hydraulic pump distributor comprises a radial force compensation groove which comprises a plate bearing face on its sides which are oriented perpendicularly to the low-pressure sealing surface on the stator side. said bearing face cooperating with a plate bearing shoulder which comprises the radial force compensation sealing plate.
  • the sealing ring for a hydraulic pump distributor comprises a radial force compensation groove which has a plate sealing face on its sides which are oriented perpendicular to the low-pressure sealing surface on the stator side. , said sealing face cooperating with a plate sealing shoulder that comprises the radial force compensation sealing plate
  • the sealing ring for hydraulic pump distributor comprises a radial force compensation sealing plate which cooperates with a sealing plate sealing lip integral or not with said plate, said lip sealing axial and / or radial and / or tangential between said plate and the radial force compensation groove.
  • the sealing ring for a hydraulic pump distributor comprises a ring sealing lip which is constituted by a flexible seal of compensation of flexible material maintained simultaneously in contact with the radial force compensation groove and with the radial force compensation sealing plate.
  • the sealing ring for a hydraulic pump distributor comprises a radial force compensation sealing plate which comprises at least one compensating peripheral contact boss arranged at its periphery, said boss having a peripheral line of contact. compensation which can come into contact with the pump rotor supply face.
  • the hydraulic pump distributor sealing ring according to the present invention comprises a plate sealing face which is positioned approximately perpendicular to the peripheral compensation contact line.
  • the hydraulic pump distributor sealing ring comprises a plate sealing face which is positioned approximately perpendicular to the compensating peripheral contact line while the plate bearing face is further away. the bottom of the radial force compensation groove and the compensating recess that said sealing face so that it is offset from the plumb line of the peripheral compensation contact line.
  • the sealing ring for a hydraulic pump distributor comprises a dispensing recess which comprises at least one connecting beam which interconnects the circumferential contact bosses, said beam thus defining on either side of its length. at least one sub-recess of distribution.
  • the sealing ring for a hydraulic pump distributor comprises rotation stop means which consist of at least one ring rotation stopper pin inserted in a stator stopper hole arranged in the pump stator on the one hand, and introduced into a ring stopper hole through the continuous sealing ring in the direction of its thickness on the other hand.
  • the sealing ring for hydraulic pump distributor 1 is provided for a hydraulic distributor 2 that may comprise a hydraulic pump 44, said distributor 2 comprising at least one pump stator distribution face 5 secured to a stator pump 3 said distribution face 5 having a low-pressure sealing surface on the stator side 12 of which open at least two inlet-discharge ports 7 arranged in the pump stator 3 and which each communicate with at least one duct d 8 which is their own and which is also arranged inside said stator 3, said distributor 2 also comprising at least one pump rotor supply face 6 integral with a pump rotor 4 said face supply 6 having a low-pressure sealing surface on the rotor side 13 from which opens at least one orifice 9 communicating with a feed duct 10 arranged the inside of said rotor 4 while the low-pressure sealing surface on the stator side 12 is positioned facing the low-pressure sealing surface on the rotor side 13 so that the supply orifice 9 is alternately facing one or other of the two intake-discharge ports 7 at least once per revolution of pumped
  • the sealing ring for hydraulic pump distributor 1 comprises at least one continuous sealing ring 11 housed at low axial and / or radial clearance in a ring groove 16 provided in the pump stator 3 inside the surface area delimited by the low-pressure sealing surface on the stator side 12, said ring 11 having a stator side face of the ring 23 housed inside the ring groove 16, and a rotor side ring face 22 which is flush with the low sealing surface -pressure stator side 12, while the inlet-discharge ports 7 open at said sealing surface 12 through said groove 16, said ring 11 being axially or radially wider than said lights 7 so covering them and comprising, approximately axially or radially aligned with the latter, at least one dispensing recess 21 passing through the continuous sealing ring 11 from one side to the other in the direction of its thickness, said recess 21 being able to put into communication the one of the two intake-discharge ports 7 with the supply port 9 when the latter is approximately facing said light 7, the same reces
  • the continuous sealing ring 11 may advantageously have a low thickness and stiffness so as to be easily deformable and to adapt to its geometric environment even when the hydraulic pressure produced by the hydraulic pump 44 is relatively low.
  • the sealing ring for hydraulic pump distributor 1 comprises at least one circumferential contact boss 14 arranged axially or radially on either side of the dispensing recess 21, said boss 14 having a line of circumferential contact 15 which can come into contact with the low-pressure sealing surface on the rotor side 13.
  • circumferential contact boss 14 and / or the low-pressure sealing surface on the rotor side 13 may be nitrided, cemented and / or coated with DLC "Diamond-like-Carbon" or any other hard coating and / or low coefficient of friction.
  • the sealing ring for a hydraulic pump distributor 1 also comprises at least one compression-decompression track 24 arranged on a certain angular sector of the rotor-side face of the ring 22, said sector being positioned outside the portion of said face 22 where is placed the radial distribution recess 21. Said track 24 is particularly visible in figure 5 .
  • the sealing ring 1 further comprises at least one ring sealing lip 39 integral or not with the contained sealing ring 11 and which provides an axial or radial seal between said ring 11 and the throat of ring 16.
  • the sealing ring for a hydraulic pump distributor 1 comprises at least one compression-decompression seal 28 which provides a seal between the face of the ring on the stator side 23 and the bottom and / or the axial sides or radial of the ring groove 16 and this, at the angular zone defined by the angular sector on which is arranged the compression-decompression track 24.
  • the sealing ring for a hydraulic pump distributor 1 comprises rotation stop means 36 shown in FIG. figures 4 and 5 which keep the continuous sealing ring 11 in a fixed angular position relative to the pump stator 3.
  • the sealing ring for a hydraulic pump distributor 1 provides that the ring groove 16 may comprise - as illustrated in FIG. figure 9 - A ring bearing face 17 on its sides which are oriented perpendicularly to the low-pressure sealing surface on the stator side 12, said bearing surface 17 cooperating with a bearing shoulder 19 that includes ring continuous ring sealing 11.
  • the ring groove 16 may comprise a ring sealing face 18 on its sides which are oriented perpendicular to the low-pressure sealing surface on the stator side 12, said sealing face 18 cooperating with a sealing shoulder of ring 20 that includes the continuous sealing ring 11.
  • the ring sealing lip 39 may be a flexible metal blade integral with the ring sealing shoulder 20.
  • ring sealing lip 39 can be positioned on, below or in the extension of the ring sealing shoulder 20.
  • the ring sealing lip 39 may consist of a lateral seal 27 of flexible material held simultaneously in contact with the ring groove 16 and with the stator-side face of the ring 23, which is clearly shown in FIG. figure 10 .
  • Said flexible material may for example be rubber or an elastomer, and may be reinforced with a more rigid material such as plastic, teflon, steel or any stiffening material or structure known to those skilled in the art .
  • the sealing ring for hydraulic pump distributor provides that the compression-decompression seal 28 may have at least one compression-decompression sector cell 25 which defines a closed and sealed volume with the ring face on the stator side 23 and the bottom and / or the axial or radial sides of the ring groove 16, said cell 25 being of round, oval, oblong, square, rectangular or any geometry, without any limitation.
  • the compression-decompression seal 28 may comprise a cellular stiffening structure 40 in which the sectoral compression-decompression cell 25 is arranged, said cellular structure 40 being made of a rigid material 42 and able to be directly or indirectly maintained. in position relative to the continuous sealing ring 11 by the rotational stop means 36, while said rigid material 42 may in all or part be coated with a flexible material 43 which can come into contact with the ring face next stator 23 on the one hand, and / or with the bottom and / or the axial or radial sides of the ring groove 16 on the other hand.
  • the honeycomb stiffening structure 40 can be integrated with the stator-side face of the ring 23 and be made in the same piece of material as the continuous sealing ring 11, in this case, the sectoral compression-decompression cell (s). 25 may be hollowed out in the stator-side face of the ring 23, for example by electrochemical machining, while the lateral seal 27 and the compression-decompression seal 28 may in particular be made of a flexible material 43 overmoulded on the face of the ring on the stator side 23 and the honeycomb stiffening structure 40, said seals then having to load only to achieve the best possible seal between the continuous seal ring 11 and the ring groove 16 with which it cooperates.
  • the sectoral compression-decompression cell (s). 25 may be hollowed out in the stator-side face of the ring 23, for example by electrochemical machining, while the lateral seal 27 and the compression-decompression seal 28 may in particular be made of a flexible material 43 overmoulded on the face of the ring on the stator side 23
  • the compression-decompression track 24 may have at least one compression-decompression sectorial orifice 26 through which a sectoral compression-decompression duct 41 opens, the latter connecting with the rotor-side face of the ring 22 the sealed and closed volume defined by FIG. sectoral compression-decompression cell 25, said sector orifice 26 being positioned in such a way that the supply orifice 9 is facing said sector orifice 26 once per revolution of the pump rotor 4, said sector orifice 26 then connecting the supply duct 10 to said sealed volume via the sectoral compression-decompression duct 41.
  • the area of the compression-decompression sector cell 25 on which said pressure is exerted is advantageously greater than the area of the section of the supply orifice 9 so that the compression-decompression track 24 is found naturally plated by said pressure on the low-pressure sealing surface on the rotor side 13 to which it faces, this resulting producing the desired seal between said track 24 and said surface 13.
  • the lateral seal 27 and the compression-decompression seal 28 may form a single piece which may be made of various rigid and flexible materials so as to be locally resistant to deformation, and so to be locally or uniformly year and / or enhanced by any means known to those skilled in the art.
  • the lateral seal 27 and / or the compression-decompression seal 28 may for example comprise a metal core 55 of rigid material 42.
  • the ring sealing face 18 can be positioned approximately vertically above the circumferential contact line 15, while a slight offset between said face 18 and said line 15 allows - as suggested by figure 10 that the pressure in the ring groove 16 plates said line 15 on the pump rotor supply face 6 to achieve a good seal between said line 15 and said feed face 6 while generating only a few contact force between these last two and therefore, little floating losses
  • the figure 10 also illustrates that the ring sealing face 18 may be positioned approximately perpendicular to the circumferential contact line 15 while the ring bearing face 17 may be further away from the bottom of the ring groove 16 and the distribution recess 21 as said sealing face 18 so that it is offset relative to the plumb with the circumferential contact line 15.
  • At least one of the axial faces of the ring groove 16 can be formed by the axial face of a ring mounting ring 34 which encloses the pump stator 3, said ring 34 allowing the mounting of the continuous ring sealing 11 and / or the compression-decompression seal 28 and / or the lateral seal 27 on the pump stator 3.
  • said mounting ring 34 can be mounted on the pump stator 3 in particular by shrinking, by gluing, by screwing, by crimping, by roller burnishing or by welding and that it can comprise at least one solid seal or viscous lodged between him and the pump stator 3.
  • the pump stator distribution face 5 and the pump rotor supply face 6 can be cylindrical while at least one of the intake-discharge ports 7 cooperates with at least one force compensation light radial 30 arranged in the pump stator 3, the latter 30 opening out from the pump stator distribution face 5 and facing the pump rotor supply face 6.
  • said compensation light 30 being furthermore located - in said stator 3 - diametrically opposite to the intake-discharge lumen 7 with which it cooperates and is connected by a radial force compensation duct 31 to the intake-discharge duct 8 to which said intake-discharge lumen 7 is connected. with which she cooperates.
  • the surface exposed by said pressure compensating light 30 is substantially equivalent to the surface exposed by the same pressure to the inlet-discharge port 7 with which it co-operates so that said pressure generates only a small amount of pressure. or no radial force on the pump stator 3 and the pump rotor 4. It is further noted that the compensation light 30 can be arranged inside the surface area delimited by the lowermost sealing surface. stator side pressure 12 while it can face the low-pressure sealing surface rotor side 13.
  • the compensating light 30 can emerge from the pump stator distribution face 5 via a radial force compensation groove 29 in which is housed a low axial play and / or tangential a force compensation sealing plate radial 32 which is for example made of steel.
  • the figure 15 shows that the radial force compensation sealing plate 32 can be traversed right through in the direction of its thickness by a compensation recess 48 which connects the radial force compensation duct 31 with the face d pump rotor supply 6.
  • the compensation recess 48 may consist of a hole of small section preserving the radial force compensation sealing plate 32 the best possible rigidity, said hole serving only to propagate to the the pump rotor supply face 6 the pressure prevailing in the radial force compensation duct 31 to which said plate 32 is connected.
  • the radial force compensation groove 29 may comprise a plate support face 49 on its sides which are oriented perpendicularly to the low-pressure sealing surface on the stator side 12, said bearing face 49 cooperating with a plate support shoulder 51 that comprises the radial force compensation sealing plate 32.
  • the radial force compensation groove 29 may comprise a plate sealing face 50 on its sides which are oriented perpendicularly to the low-pressure sealing surface on the stator side 12, said sealing face 50 cooperating with a plate sealing shoulder 52 that comprises the radial force compensation sealing plate 32.
  • the radial force compensation sealing plate 32 can cooperate with a compensation plate sealing lip 45 which may or may not be integral with said plate 32, said lip 45 providing axial and / or radial sealing and / or tangential between said plate 32 and the radial force compensation groove 29 while said lip 45 may in particular be a flexible metal blade integral with the plate sealing shoulder 52 and / or be positioned on, below or in the extension of said shoulder 52.
  • the ring sealing lip 39 may consist of a flexible sealing gasket 33 of flexible material held simultaneously in contact with the radial force compensation groove 29 and with the sealing plate of radial force compensation 32 said flexible material may for example be rubber or an elastomer, and may be armed with a more rigid material such as plastic, Teflon, steel or any material or stiffening structure known to the skilled in the art.
  • the radial force compensation sealing plate 32 may comprise at least one peripheral compensation contact boss 46 arranged at its periphery, said boss 46 having a peripheral compensation contact line 47 able to come into contact with the face of the device. pump rotor supply 6.
  • peripheral compensation contact boss 46 and / or the low-pressure sealing surface on the rotor side 13 with which it cooperates can be nitrided, cemented and / or coated with DLC "Diamond-like-Carbon" or any other hard coating and / or low coefficient of friction.
  • the plate sealing face 50 can be positioned approximately perpendicular to the peripheral compensating contact line 47, while a slight offset between said face 50 and said line 47 allows the pressure in the throat of compensation of radial force 29 plate said line 47 on the pump rotor supply face 6 to achieve a good seal between said line 47 and said feed face 6 while generating little contact force between these last two and therefore, little friction losses, This configuration is clearly exposed in figure 15 .
  • the figure 15 also shows that the plated sealing face 50 can be positioned approximately perpendicular to the compensating peripheral contact line 47 while the plate bearing face 49 is further away from the bottom of the compensation groove of FIG. radial force 29 and the compensating recess 48 that said sealing face 50 so that it is offset from the plumb with the peripheral compensating contact line 47.
  • the distribution recess 21 may comprise at least one connecting beam 56 which interconnects the circumferential contact bosses 14, said beam 56 thus defining on either side of its length at least one distribution sub-recess 57 said beam 56 thus partially closing the intake-discharge lumen 7 which is approximately axially or radially aligned with said recess 21 without compromising the good circulation of a hydraulic fluid or any other fluid between said lumen 7 and the orifice feeding 9 facing him.
  • the rotational stop means 36 may consist of at least one ring rotation stop pin 35 plugged into a stator stop pin hole 37 provided in the pump stator 3 on the one hand, and introduced into a ring stop pin hole 38 through the continuous sealing ring 11 in the direction of its thickness on the other hand.
  • the ring rotation stop pin 35 can be freely mounted in the ring stop pin hole 38 and clamped in the stator stop pin hole. 37 or vice versa, said stop pin 35 being for example a metal cylinder or a split elastic pin.
  • the pump stator distribution face 5 and the pump rotor supply face 6 are cylindrical. Said ring 1 is therefore also of predominantly cylindrical shape.
  • the hydraulic distributor 2 comprises according to this example two inlet-discharge ports 7. This justifies that the continuous seal ring 11 has two distribution recesses 21 each radially aligned with the inlet-discharge ports 7 with which it cooperates as shown by Figures 3 to 8 and 12 and 13 .
  • the figure 10 is a partial section along BB of the continuous sealing ring 11 shown in FIG. figure 8 .
  • Said cut is made at a dispensing recess 21 and more particularly at a dispensing sub-recess 57.
  • Said cut shows in particular the circumferential contact boss 14 arranged axially on either side of said obviously 21.
  • said boss 14 has a circumferential contact line 15 intended to come into contact with the low-pressure sealing surface on the rotor side 13 so as to achieve with the latter the best possible seal.
  • the dispensing recesses 21 pass through the continuous sealing ring 11 from one end to the other in the direction of its thickness and are separated from each other in the circumferential direction by a compression-decompression track 24 on the surface of which open several sector-specific compression-decompression ducts 41 via a sectoral orifice of compression-decompression 26 own.
  • the circumferential contact bosses 14 arranged axially on either side of the distribution recesses 21 are connected in the axial direction by connecting beams 56 which separate the distribution sub-recesses 57.
  • each compression-decompression sector duct 41 is connected to a sectoral compression-decompression cell 25 which defines, with the bottom of the ring groove 16, a sealed and sealed volume.
  • the figure 11 is a partial section along CC of the continuous sealing ring 11 shown in FIG. figure 8 which shows in detail how a sectoral compression-decompression cell 25 is arranged and how it is connected to the surface of the compression-decompression track 24 by the sectoral compression-decompression duct 41 with which it cooperates.
  • the compression-decompression sector cells 25 are arranged in a stiffening honeycomb structure 40 integrated with the stator side ring face 23, said structure 40 forming - with a flexible material 43 overmolded on said structure - the compression seal -depression 28, as shown in more detail the figure 11 .
  • the two compression-decompression seals 28 and the four side seals 27 comprise in particular of the same continuous piece of flexible material 43.
  • said continuous piece is shown separate from the continuous sealing ring 11.
  • said piece can be coated by overmolding or by gluing the face next to the stator ring 23 and the stiffening honeycomb structure 40 integrated in said ring face 23.
  • the figure 11 shows that the flexible material 43 partially fills the sectoral compression-decompression alveoli 25 so as to form a pocket in said alveoles 25, and makes the best possible seal between the face of the stator side ring 23 and the ring groove 16.
  • the continuous sealing ring 11 is held in a fixed angular position relative to the pump stator 3 by the ring rotation stop pin 35 - here a simple metal cylinder - which passes through said ring 11 via the pawn hole ring stop 38, said pin 35 being free in said hole 38 while it is locked in the stator stop pin hole 37.
  • each intake-discharge lamp 7 cooperates with the two radial force compensation holes 30 which are arranged at its diametrical opposite in the pump stator 3, the latter slots 30 being connected by their compensation pipe.
  • the total area exposed to pressure by the two so-called compensation windows 30 is substantially equivalent to the surface exposed at the same pressure to the intake-discharge port 7 with which they cooperate.
  • the pressure in the intake-discharge port 7 generates a radial force on the pump stator 3 and the pump rotor 4 weak or zero.
  • each radial force compensation light 30 also provides the best possible seal between said light 30 and said supply face 6.
  • the radial force compensation sealing plate 32 comprises in particular a compensation plate sealing lip 45 which provides a seal between said plate 32 and the radial force compensation groove 29 with which it cooperates.
  • the figure 14 which is a three-dimensional section of said plate 32 and the figure 15 which is a schematic section show that, in the case taken here to illustrate the operation of the sealing ring 1 according to the invention, the compensation plate sealing lip 45 is a thin metal blade arranged in the extension of the plate sealing shoulder 52 and which cooperates with a flexible seal of compensating seal 33 of flexible material 43 such as rubber or an elastomer, said flexible material 43 being able to be overmolded under the sealing plate radial force compensation device 32 and in extension of said shoulder 52, said flexible seal 33 being held simultaneously in contact with the radial force compensation groove 29 and with the lower part of the compensation plate sealing lip 45 .
  • the radial force compensation sealing plate 32 is relatively flexible and easily deformable so that the pressure can press the peripheral compensation contact line 47 on the low-pressure sealing surface on the rotor side. 13.
  • an offset is provided between the plate sealing face 50 that has the radial force compensation groove 29 and the plumb with the compensating peripheral contact line 47 that comprises - immediately above said sealing face 50 - the radial force compensation sealing plate 32. It results from said shift a weak section S1 on which the pressure is exerted, so that the radial force resulting from said section S1 remains low. This tends to achieve a good seal between the peripheral compensating contact line 47 and the low-pressure sealing surface on the side rotor 13 while generating little contact force between said line 47 and said surface 13 and therefore, little loss by floating.
  • the continued seal ring 11 is of small thickness and as such, it is also relatively flexible and easily deformable. Furthermore, it should also be noted that the ring groove 16 is deep enough for said continuous ring 11 to be radially offset relative to said groove 16, as shown by FIGS. Figures 12 and 13 .
  • the deformations and eccentrations to which the continuous sealing ring 11 is subjected are of the order of a few microns to a few tens of microns and that the Figures 12 and 13 which show said deformations and eccentrations strongly exaggerate them so that we can understand the impact on the operation of the sealing ring 1 according to the invention.
  • the highest pressure prevails, for example a thousand bars, while a lower pressure prevails in the lower lumen, for example ten bars, the highest pressure exerts a local radial thrust. on the side of the ring stator 23 whose intensity is stronger than that exerted on said face 23 the lower pressure at the level of the lower lumen 7.
  • the continuous sealing ring 11 is deformed and is pressed against the low-pressure sealing surface on the rotor side 13 at the level of the upper lumen 7 while said continuous ring 11 remains at a distance a few microns or tens of microns of said surface 13 at the level of the lower lumen 7.
  • the axial offset provided between the two ring sealing faces 18 and the plumb with the circumferential contact lines 15 and which determines the section S1 makes the pressure in the ring groove 16 actually plates said lines 15 on the pump rotor supply face 6. This tends to seal between said lines 15 and said feed face 6 while generating little contact force between said lines 15 and said face 6 and therefore, little loss by friction.
  • the contact pressure between said lines 15 and the pump rotor supply face 6 depends essentially on the width of the contact made by said lines 15 with said face 6, said width also resulting from a voluntary choice made during of the design of the continuous sealing ring 11.
  • the seal is formed on the one hand by the lip of the ring sealing ring 39 which remains in contact - given its elasticity - with the ring sealing face 18, and secondly, by the lateral seal 27.
  • said lip 39 prevents said seal 27 from Extrude even under very high pressure - for example two thousand bars - while the latter ensures a perfect seal.
  • FIG 13 shows the deformation of the continuous sealing ring 11 when it is in the upper lumen 7 that the weakest pressure prevails - for example ten bars - while it is in the lower lumen 7 that the highest pressure prevails - For example a thousand bars, the operation of the continuous sealing ring 11 remains unchanged.
  • the hydraulic pump cylinders 54 draw oil under ten bars from the lower slot 7 to push it back under a thousand bars at the level of the upper light 7. Also, during the passage of any supply port 9 of the upper lumen 7 to the lower lumen 7 via the compression-decompression track 24, it is necessary to progressively relax the oil included in the hydraulic pump cylinder 54 and the supply ducts 10 which are connected to said supply port 9. During this expansion, the energy that has been stored by said oil during its compression - said oil being compressible - can be mechanically recovered by the hydraulic pump 44. This function is necessary to give said pump 44 a good energy efficiency.
  • the feed orifice 9 continues to engage on the compression-decompression track 24 until it encounters a first sectoral pressure-decompression orifice 26 which connects said track 24 to the sealed and sealed volume defined by the sectoral cell of compression-decompression 25 located immediately below said sector orifice 26.
  • the compression-decompression track 24 is pressed by the pressure on the low-pressure sealing surface on the side 13 of which opens the opening of the feed port 9. This constitutes a seal around of the supply port 9 between the compression-decompression track 24 and the low-pressure sealing surface on the rotor side 13, with a plating force of said track 24 on said surface 13 which is all the more important as the pressure prevailing in the hydraulic pump cylinder 54 is high.
  • the annular gap between two compression-decompression sector openings 26 and the diameter of said orifices is calculated so that a same supply orifice 9 can not be simultaneously facing two said sectoral orifices 26.
  • the number of compression-decompression sector orifice 26 it is noted that one can provide axially oblong axial supply ports 9, which can be staggered in at least two rows, the latter configuration also being applicable to As a non-limiting example - to the sectoral compression-decompression ports 26.
  • the geometry of the sectoral cells of compression-decompression 25 presented in particular in figure 5 is non-limiting and may differ from one cell 25 to another.
  • the choice of said geometry must be guided by the need on the one hand, to produce the best possible seal between the compression-decompression track 24 and the low-pressure sealing surface on the rotor side 13 and other on the other hand, to generate the lowest possible friction between said track 24 and said surface 13.
EP14796176.7A 2013-09-25 2014-09-22 Bague d'étanchéité pour distributeur de pompe hydraulique Active EP3049671B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1359250A FR3011045B1 (fr) 2013-09-25 2013-09-25 Bague d'etancheite pour distributeur de pompe hydraulique
PCT/FR2014/052352 WO2015044571A1 (fr) 2013-09-25 2014-09-22 Bague d'étanchéité pour distributeur de pompe hydraulique

Publications (2)

Publication Number Publication Date
EP3049671A1 EP3049671A1 (fr) 2016-08-03
EP3049671B1 true EP3049671B1 (fr) 2018-03-14

Family

ID=49998376

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14796176.7A Active EP3049671B1 (fr) 2013-09-25 2014-09-22 Bague d'étanchéité pour distributeur de pompe hydraulique

Country Status (9)

Country Link
EP (1) EP3049671B1 (ja)
JP (1) JP6387088B2 (ja)
KR (1) KR102254259B1 (ja)
CN (1) CN105593519B (ja)
AU (1) AU2014326490B2 (ja)
CA (1) CA2925485C (ja)
ES (1) ES2670551T3 (ja)
FR (1) FR3011045B1 (ja)
WO (1) WO2015044571A1 (ja)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106352090B (zh) * 2016-08-31 2017-09-29 李泓涵 密封圈及密封圈生产模具
US11448203B2 (en) 2016-09-09 2022-09-20 Eaton Intelligent Power Limited Hydraulic radial piston device
CN109989898A (zh) * 2019-05-15 2019-07-09 梁德荣 倾斜密封环配流机构、轴向柱塞马达及轴向柱塞泵

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1354562A (fr) 1963-04-11 1964-03-06 élément de guide d'onde non réciproque
JPS627672A (ja) * 1985-07-04 1987-01-14 株式会社　香蘭社 繊維強化された窒化ケイ素セラミツクの製造方法
EP0263218B1 (fr) * 1986-10-08 1990-01-03 POCLAIN HYDRAULICS Société Anonyme de droit français Mécanisme hydraulique comportant des glace et contre-glace de distribution du fluide
FR2679963B1 (fr) * 1991-08-01 1993-11-12 Poclain Hydraulics Mecanisme a fluide sous pression muni d'enceintes d'equilibrage particulieres.
JP2002130589A (ja) * 2000-10-24 2002-05-09 Nsk Ltd 主軸の潤滑装置
DE102005015905A1 (de) * 2005-04-07 2006-10-12 Linde Ag Anordnung mit einem Schwungrad einer Brennkraftmaschine und mit einer dazu benachbarten hydrostatischen Pumpe
DE102007024174B4 (de) * 2006-12-11 2022-09-08 Robert Bosch Gmbh Axialkolbenmaschine mit einer Verdrehsicherung für die Steuerplatte
DE102008043993B3 (de) * 2008-11-21 2010-04-29 Thielert Aircraft Engines Gmbh Common-Rail-Hochdruckpumpe
DE102008060067B4 (de) * 2008-12-02 2017-11-02 Robert Bosch Gmbh Axialkolbenmaschine mit einer Steuerplatte, die in einem Teilbereich des äußeren Dichtstegs eine erhöhte Elastizität aufweist
CN101539129B (zh) * 2009-04-24 2013-04-24 上海纳博特斯克液压有限公司 一种轴式液压柱塞泵或马达

Also Published As

Publication number Publication date
KR20160058901A (ko) 2016-05-25
WO2015044571A1 (fr) 2015-04-02
JP2016539285A (ja) 2016-12-15
EP3049671A1 (fr) 2016-08-03
CA2925485C (fr) 2019-04-02
CN105593519B (zh) 2017-10-24
CA2925485A1 (fr) 2015-04-02
FR3011045A1 (fr) 2015-03-27
ES2670551T3 (es) 2018-05-30
KR102254259B1 (ko) 2021-05-20
JP6387088B2 (ja) 2018-09-05
FR3011045B1 (fr) 2015-10-30
CN105593519A (zh) 2016-05-18
AU2014326490B2 (en) 2018-01-25
AU2014326490A1 (en) 2016-05-12

Similar Documents

Publication Publication Date Title
EP2425100B1 (fr) Cale d'aube de soufflante avec un élastomère
EP3049671B1 (fr) Bague d'étanchéité pour distributeur de pompe hydraulique
FR2914372A1 (fr) Pompe equilibree a palettes a cylindree variable avec joints d'etancheite de face flottants et joints d'etancheite de pa lette sollicites
FR2631081A1 (fr) Pompe a membrane annulaire
FR3011290A3 (fr) Pompe a engrenages a deplacement positif
FR3096096A1 (fr) Pompe à vide primaire sèche
FR3031786A1 (fr) Integration d'une pompe en fut de pignon
CA2464335C (fr) Machine volumetrique rotative
FR2617543A1 (fr) Pompe turbomoleculaire
WO2017109329A1 (fr) Système de refroidissement et lubrification pour dispositif d'étanchéité pour piston
FR2862354A1 (fr) Pompe a cylindree variable, en particulier pompe a palettes
EP0618365B1 (fr) Machine volumétrique à guidage magnétique
EP0736691B1 (fr) Pompe volumétrique rotative à gerotor à alimentation radiale
EP0534836B1 (fr) Machine hydraulique du type à engrenages à corps flottant
FR2564907A1 (fr) Machine a fluide du type rotatif
FR2992693A1 (fr) Pompe a engrenage interne double
EP3152472A1 (fr) Raccord d'etancheite tournant haute-pression a bague continue extensible
FR2665221A1 (fr) Pompe a engrenages a denture interieure, sans piece intermediaire en forme de faucille.
FR3106630A1 (fr) Pompe à vide sèche
FR2755490A1 (fr) Assemblage a joint d'etancheite
FR2995945A1 (fr) Pompe a engrenage interieur, notamment pour une installation de freinage hydraulique de vehicule
FR3068089A3 (fr) Pompe a eau
FR2981993A1 (fr) Pompe a engrenages a cylindree variable pour turbomachine d'aeronef
FR2492904A2 (fr) Perfectionnements aux pompes et moteurs a fluide a engrenages
FR3005106A1 (fr) Machine volumique rotative a trois pistons

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20160422

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
17Q First examination report despatched

Effective date: 20170201

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20170809

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 979164

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180315

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: FRENCH

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602014022404

Country of ref document: DE

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2670551

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20180530

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20180314

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180614

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 979164

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180314

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180614

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180615

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 5

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602014022404

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180716

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

26N No opposition filed

Effective date: 20181217

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20180930

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180922

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180922

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20140922

Ref country code: MK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180314

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180714

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20230921

Year of fee payment: 10

Ref country code: GB

Payment date: 20230927

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20230927

Year of fee payment: 10

Ref country code: FR

Payment date: 20230928

Year of fee payment: 10

Ref country code: DE

Payment date: 20230927

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20231002

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20231004

Year of fee payment: 10