EP1592887B1 - Pompe haute pression - Google Patents

Pompe haute pression Download PDF

Info

Publication number
EP1592887B1
EP1592887B1 EP03773421A EP03773421A EP1592887B1 EP 1592887 B1 EP1592887 B1 EP 1592887B1 EP 03773421 A EP03773421 A EP 03773421A EP 03773421 A EP03773421 A EP 03773421A EP 1592887 B1 EP1592887 B1 EP 1592887B1
Authority
EP
European Patent Office
Prior art keywords
piston
high pressure
pressure pump
pump according
chamber
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.)
Expired - Lifetime
Application number
EP03773421A
Other languages
German (de)
English (en)
Other versions
EP1592887A1 (fr
Inventor
Marco Ganser
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.)
Ganser Hydromag AG
Original Assignee
Ganser Hydromag AG
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 Ganser Hydromag AG filed Critical Ganser Hydromag AG
Priority to EP06026525.3A priority Critical patent/EP1760312B1/fr
Publication of EP1592887A1 publication Critical patent/EP1592887A1/fr
Application granted granted Critical
Publication of EP1592887B1 publication Critical patent/EP1592887B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • 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
    • F04B1/0408—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—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
    • F04B1/0413—Cams
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/04—Draining
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for

Definitions

  • the invention relates to a high pressure pump according to the preamble of claim 1, which is particularly suitable for use in a fuel injection system for internal combustion engines.
  • a generic high-pressure pump for a fuel injection device for internal combustion engines in which the piston of a piston pump unit is driven harmoniously by an eccentric drive.
  • the piston carries at its end facing away from the working space of the piston pump unit end a sliding shoe, which rests with a sliding surface on a sliding bearing surface of a lifting ring.
  • the cam ring is rotatably mounted on an eccentric pin of a drive shaft and is driven revolving, but not rotating.
  • the drive shaft, the eccentric pin, the cam ring and the shoe are housed in a low pressure space, which serves as a feed space for the medium to be conveyed, i. Fuel, serves.
  • a relief space is formed, which is open to the sliding bearing surface and via a passage which extends in the longitudinal direction of the pump piston, with the working space is in direct hydraulic communication. The discharge space is therefore filled with the fuel to be delivered.
  • the lubrication of the sliding bearing between the shoe and the cam ring is effected by the fuel in the discharge chamber.
  • the bearing between the eccentric pin and the cam ring is lubricated by the located in the low-pressure space fuel.
  • fuel is known to have poor lubricating properties and therefore can only develop a limited lubricating effect.
  • the present invention is now based on the object to provide a high-pressure pump of the type mentioned for very high discharge pressures and large flow rates, the production costs are as low as possible and can meet the high demands on the reliability and life.
  • the medium to be pumped which is eg fuel
  • the medium to be pumped is separated from the medium in the discharge space. It is therefore no longer limited to use the medium to be pumped for the pressure relief and lubrication of the sliding bearing between the cam and the piston. Rather, a much more suitable for these tasks medium can be selected, ie a such with excellent lubricating properties, eg lubricating oil.
  • a much more suitable for these tasks medium can be selected, ie a such with excellent lubricating properties, eg lubricating oil.
  • the high-pressure pump 1 shown in FIGS. 1 to 4 which is intended for use in a fuel injection system for internal combustion engines, has two diametrically opposed piston pump units 2, 2 '(plunger pump units), which have the same design and operate in push-pull.
  • Each piston pump unit 2, 2 ' has a housing block 3, which is fixedly connected to a pump housing 4 and projects into the interior 5 of this pump housing 4.
  • Each piston pump unit 2, 2 ' has a piston 6 (plunger), which is guided with a tight sliding fit in a cylinder bore 7 in the housing block 3 linearly movable.
  • the piston 6 bounded with an end face 6a a working space 8 and extends at its opposite end to a foot part 9.
  • This foot part 9 has a flat sliding surface 10 which rests on a sliding bearing surface 11 which is provided on a cam ring 12.
  • This cam ring 12 is common to both piston pump units 2, 2 '.
  • a crank drive 13 is provided which has a drive shaft 14 shown in dashed lines and an eccentric element 15 fixedly connected thereto.
  • the drive shaft 14 is driven circumferentially about its axis of rotation 14a (FIG. 1).
  • the eccentric element 15 is arranged with an eccentricity e (FIG. 1) with respect to the axis of rotation 14a of the drive shaft 14.
  • the cam ring 12 When rotating the drive shaft 14, the cam ring 12 is moved on the one hand parallel to the slide bearing surfaces 11 and on the other hand perpendicular to the axis of rotation 14a of the drive shaft 14, in each direction by the amount 2e. The cam ring 12 is thus displaced in operation relative to the foot part 9 of the piston 6 back and forth.
  • an inlet line 18 is formed, which communicates with the working space 8 via a pressure-controlled inlet valve 19 (FIG. 1).
  • the inlet line 18 is connected to a supply line, not shown, which is connected to a liquid reservoir, ie in the present case with a fuel tank, for example via a prefeed pump.
  • an outlet line 20 is further provided, which via a pressure-controlled Outlet valve 21 is connected to the working space 8 (Fig. 1).
  • the outlet conduit 20 is connected to a high pressure space, eg the common rail of a fuel injection system.
  • a relief space 22 is formed in the foot part 9 of the piston 6, which is open to the sliding bearing surface 11.
  • a continuous, coaxial passage 23 which is open on the one hand to the working space 8 and on the other hand to the discharge space 22 (the passage 23 could also be desachsiert).
  • This passage 23 whose diameter changes, includes a longitudinal bore 24 in which a control piston 25 is slidably guided with a tight sliding fit, which serves as a pressure transmission element.
  • the control piston 25 rests on a compression spring 26, which is supported at the other end on a spring ring 27 (FIG. 2), which is held in the piston 6.
  • annular groove 28 is formed, which extends around the piston 6 around and to the cylinder bore 7 is open.
  • a transverse bore 29 is present, which passes through the piston 6 and which is connected at both ends with the annular groove 28.
  • a drain line 30 is connected, which runs in the housing block 3 and which is connected to a return line, not shown, which leads to a collecting reservoir, which may be the fuel tank.
  • a collecting reservoir which may be the fuel tank.
  • the eccentric element 15 is provided with a lubrication groove 31 which extends along a part of the circumference and is open towards the cam ring 12.
  • the lubrication groove 31 is connected via a radial bore 32 in the eccentric element 15 with a feed channel 33 which extends in the direction of the axis of rotation 14a of the drive shaft 14 and which is connected via a lubricant pump, not shown, with a lubricant reservoir.
  • a lubricant preferably lubricating oil, with a pressure of e.g. 2 - 6 bar supplied.
  • two connecting channels 34, 35 are formed, each of which leads from the inner surface 12 a of the cam ring 12 to one of the sliding bearing surfaces 11.
  • the lubrication groove 31, which is permanently connected to the feed channel 33 is only in certain rotational positions of the eccentric element 15 with a connecting channel 34, 35 in combination, as shown in FIGS. 1-3.
  • connection channels 34, 35 are not in connection with the lubrication groove 31 nor with the associated relief space 22.
  • FIGS. 3 and 4 the situation after a rotation of the drive shaft 14 is shown by now a total of 270 °.
  • the piston 6 has reached its center position during the suction stroke.
  • the lifting ring 12 now assumes its left end position, which is shown in Fig. 4 in solid lines.
  • This Fig. 4 shows that the cam ring 12 in the direction of the sliding bearing surface 11 performs a total stroke C, which is equal to 2e, so the double eccentricity e.
  • left end position of the cam ring 12 is now the connecting channel 34 in the cam ring 12 with the discharge chamber 22 and the lubrication 31 in connection.
  • liquid i. Fuel
  • Lubricant i. Lubricating oil
  • This leakage liquid is used as a liquid-lubricant mixture, i. as a fuel-lubricating oil mixture, collected in the annular groove 28.
  • liquid (fuel) from the working space 8 over the upper portion of the passage 23 and through the very small gap between the control piston 25 and the wall of the longitudinal bore 24 can pass.
  • This leakage liquid passes through the transverse bore 29 in the piston 6 also in the annular groove 28.
  • lubricant lubricating oil
  • This leak lubricant also passes via the transverse bore 29 into the annular groove 28.
  • the mixture of liquid (fuel and lubricant (lubricating oil)) in the annular groove 28 is led away via the drain line 30 and is e.g. into the liquid reservoir, i. the fuel tank, returned.
  • annular groove 36 is additionally formed coaxial with the relief space 22 and to slide bearing surface 11 is open.
  • This annular groove 36 communicates with a cam ring 12 formed in the sliding surface 10 toward open longitudinal groove 37 in conjunction.
  • This longitudinal groove 37 is offset relative to the sectional plane of Fig. 3 (which is perpendicular to the rotation axis 14a and in the middle of the cam ring 12) in the direction of the axis of rotation 14a of the drive shaft 14 and opens at both ends into the interior 5 of the pump housing 4 (Fig. 4).
  • the leakage liquid (lubricating oil) entering this annular groove 36 is returned to the interior 5 via the longitudinal groove 37.
  • the second embodiment of a high-pressure pump 1 'shown in FIG. 5 differs from the first embodiment according to FIGS. 1-4 by another embodiment of the pressure-transmitting element arranged in the piston 6.
  • Fig. 5 which corresponds to the representation of FIG. 2, the same reference numerals are used for parts that are the same in both embodiments as in Figs. 1-4.
  • the piston 6 consists of a piston element 38 guided in the cylinder bore 7 and a ring 39 which is fixedly connected to the end of the piston element 38 at the working space 8, e.g. by pressing or shrinking.
  • the ring 39 rests with a sliding surface 10 on the sliding bearing surface 11 on the cam ring 12 and has a flange 40 on which the compression spring 17 is supported.
  • This compression spring 17 ensures - as described with reference to FIGS. 1 - 3 - that the ring 39 remains in contact with the cam ring 12.
  • the sliding surface 10 is formed on the ring 39.
  • the flange 40 could also be formed as a separate part, analogous to the bearing ring 16 of FIG. 2.
  • an elastically deflectable membrane 41 is arranged, which is clamped sealingly along its edge region between the ring 39 and the piston member 38.
  • This membrane 41 which serves as a pressure-transmitting element, spans the relief space 22 bounded by the inner annular wall 39a and separates this relief space 22 from a chamber 42 formed in the piston element 38
  • This chamber 42 opens into a longitudinal bore 43 which extends in the direction of the longitudinal axis of the piston element 38 and via which the chamber 42 communicates with the working space 8.
  • the longitudinal bore 43 and the chamber 42 form the passage 23.
  • the chamber 42 is filled with the liquid to be conveyed, ie with fuel.
  • the pressure in the chamber 42 changes in the same direction as the pressure in the working space 8.
  • the diaphragm 41 is moved downwards in the direction of pressurization, i. to slide bearing surface 11 out, deflected. This leads to an increase in pressure in the lubricant-containing relief space 22 and thus to a hydrostatic pressure relief, as already described with reference to FIGS. 1-4. Since the pressures on both sides of the diaphragm 41 are practically the same, the stress on the diaphragm 41 is low. This can thus be thin-walled and elastic.
  • annular groove 28 which is present in the first exemplary embodiment according to FIGS. 1-3, together with the outflow line 30 for collecting and removing leakage fluid is not shown, but can also be provided if required.
  • the membrane 41 is attached to the working space 8 facing end surface 6a of the piston 6.
  • the attachment of the membrane 41 could take place by welding the same or, analogously to FIG. 5, with a screwed, pressed or shrunk holding part.
  • the passage 23 is then below the membrane 41, it is filled with the lubricant and communicates directly with the relief space 22nd
  • the mode of operation of the embodiment shown in FIG. 5 corresponds to the mode of operation described with reference to FIGS.
  • a high-pressure pump 1, 1 ' according to the invention described in connection with FIGS. 1-5 have the advantage that by arranging a pressure-transmitting element, i. a control piston 25 or a membrane 41, in the working space 8 and the discharge chamber 22 connecting passage 23, the media in the working space 8 and the discharge chamber 22 are separated from each other.
  • a pressure-transmitting element i. a control piston 25 or a membrane 41
  • the media in the working space 8 and the discharge chamber 22 are separated from each other.
  • a suitable lubricant in the region of the cam ring 12 and the crank drive 13, regardless of the medium to be pumped (fuel).
  • the desired pressure relief of the sliding bearing which is formed by the sliding surface 10 on the piston 6 and the sliding bearing surface 11 on the cam ring 12, achieved without great design effort.
  • the piston 6 has no transverse bore 29.
  • control piston 25 has a larger diameter than shown in FIGS. 1-3.
  • the longitudinal bore 24 for guiding the control piston 25 in close sliding fit can be open towards the top in the direction of the working chamber 8.
  • the narrower in cross section part of the passage 23 is again below the control piston 25 and communicates directly with the relief chamber 22.
  • the control piston 25 is installed from above into the piston 6.
  • a spring ring, analogous to the spring ring 27 according to FIG. 2 then prevents the control piston from exiting above the end surface 6a.
  • the longitudinal bore 24 can also be continuous in the piston 6.
  • the remaining part of the passage 23 has the same diameter as the longitudinal bore 24. It is also conceivable to form the remaining portion of the passage 23 slightly larger than the diameter of the longitudinal bore 24.
  • the inner surface 12a of the cam ring 12, together with the associated surface of the Exenterides 15, in the direction of the rotation axis 14a slightly convex or even slightly longitudinal in the longitudinal and transverse directions. In this case, it is recommended to design the cam ring 12 in two parts for assembly reasons.
  • piston pump unit 2 instead of two piston pump units 2, 2 'as shown in FIG. 1, only one piston pump unit 2 can be provided.
  • more than two piston pump units with corresponding sliding surfaces 11 of the cam ring 12 can be radially mounted, e.g. 3 by 120 °, or 4 by 90 °, or 6 offset by 60 ° piston pump units with a common cam ring 12th
  • high-pressure pumps 1, 1 are intended for use in fuel injection systems of internal combustion engines, in particular of diesel engines, these pumps can also be used in other fields.
  • control piston 25 it is also possible to form the control piston 25 with two different diameters. If the end face facing the working space 8 is then larger than the one facing the relief space, a pressure transmission takes place. In the opposite case, a pressure reduction. In these embodiments, it may be advantageous to form the control piston 25 of two separate parts, each with the appropriate diameter. If the holes with the correspondingly larger diameter and those with the corresponding smaller diameter are not precisely aligned, tolerance and friction problems can thus be prevented.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Superconductors And Manufacturing Methods Therefor (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (20)

  1. Pompe haute pression, notamment pour un système d'injection de carburant pour moteurs à combustion interne, comprenant au moins une unité de pompe à piston (2, 2') qui présente un piston (6) guidé dans un alésage de cylindre (7), délimitant une chambre de travail (8), avec un entraînement de vilebrequin (13) pour l'entraînement du piston (6), avec un anneau de levage (12) disposé entre l'entraînement de vilebrequin (13) et le piston (6) qui est monté de manière rotative par rapport à l'entraînement de vilebrequin (13) mais non entraîné en rotation, et qui présente une surface de palier lisse plane (11), sur laquelle le piston (6) est supporté avec une surface de glissement (10), et avec une chambre de décharge (22) ouverte vers la surface de palier lisse (11) et prévue dans la région de la surface de glissement (10), qui est en liaison de pression avec la chambre de travail (8) par le biais d'un passage (23) réalisé dans le piston (6), caractérisée en ce qu'un élément de transfert de pression (25, 41) est disposé dans le passage (23) dans le piston (6), lequel peut être sollicité d'un côté par le fluide à refouler et du côté opposé par un fluide sous pression dans la chambre de décharge (22), peut être déplacé sous l'effet de la pression dans la direction de la sollicitation par pression et sépare la communication fluidique entre la chambre de décharge (22) et la chambre de travail (8).
  2. Pompe haute pression selon la revendication 1, caractérisée en ce que l'entraînement de vilebrequin (13) présente un élément d'excentrique (15) avec une certaine excentricité (e) disposé sur un arbre d'entraînement (14) pouvant être entraîné en rotation, sur lequel l'anneau de levage (12) est monté sans tourner en même temps.
  3. Pompe haute pression selon la revendication 1 ou 2, caractérisée en ce que l'élément de transfert de pression est un piston de commande (25) qui est guidé de manière déplaçable et avec un glissement étroit dans un alésage longitudinal (24) appartenant au passage (23).
  4. Pompe haute pression selon la revendication 3, caractérisée en ce que le piston de commande (6) est supporté au niveau de son côté frontal tourné vers la chambre de décharge (22) sur un ressort de pression (26) qui s'applique à l'autre extrémité sur une butée.
  5. Pompe haute pression selon la revendication 4, caractérisée en ce que la butée est formée par un élément de support maintenu dans le piston de commande (25), notamment une rondelle-ressort (27).
  6. Pompe haute pression selon la revendication 1 ou 2, caractérisée en ce que l'élément de transfert de pression est une membrane déformable élastiquement (41) qui est tendue en travers du passage (23) et qui est fixée dans sa région marginale de manière hermétique.
  7. Pompe haute pression selon la revendication 6, caractérisée en ce que le piston (6) présente un élément de piston (38) guidé dans l'alésage longitudinal (7) et une bague (39) qui est connectée à l'élément de piston (38) au niveau de l'extrémité de l'élément de piston (38) opposée à la chambre de travail (8).
  8. Pompe haute pression selon la revendication 7, caractérisée en ce que la membrane (41) est fixée dans sa région marginale entre l'élément de piston (38) et la bague (39).
  9. Pompe haute pression selon l'une quelconque des revendications 3 à 5, caractérisée en ce qu'une rainure annulaire (36) entourant coaxialement la chambre de décharge (22) est réalisée dans le piston (6), est ouverte vers la surface de palier lisse (11) et est en liaison avec un espace (5) dans lequel sont montés l'entraînement de vilebrequin (13) et l'anneau de levage (12).
  10. Pompe haute pression selon la revendication 9, caractérisée en ce qu'une rainure longitudinale (37) débouchant dans l'espace (5), ouverte vers la surface de glissement (10), est réalisée dans l'anneau de levage (12) dans la région de la surface de palier lisse (11), est décalée dans la direction de l'axe de rotation (14a) de l'arbre d'entraînement (14) par rapport à la chambre de décharge (22) et communique avec la rainure annulaire (36).
  11. Pompe haute pression selon l'une quelconque des revendications 1 à 10, caractérisée en ce que le fluide sous pression dans la chambre de décharge (22) est un agent lubrifiant, de préférence de l'huile lubrifiante.
  12. Pompe haute pression selon la revendication 11, caractérisée en ce qu'un canal de connexion (34, 35) est réalisé dans l'anneau de levage (12) et débouche dans la surface de palier lisse (11) en un endroit tel qu'il soit connecté à la chambre de décharge (22) uniquement dans des positions déterminées de l'anneau de levage (12) par rapport au piston (6) et qu'il puisse être raccordé périodiquement à une conduite d'amenée d'agent lubrifiant (31, 32, 33).
  13. Pompe haute pression selon la revendication 12, caractérisée en ce que le canal de connexion (34, 35) débouche à l'autre extrémité dans la surface interne (12a) de l'anneau de levage (12) en contact avec l'excentrique (15) de l'entraînement de vilebrequin (13) et en ce qu'une rainure de lubrification (31) ouverte vers l'extérieur est prévue sur la périphérie de l'excentrique (15), s'étend sur une partie de sa périphérie et est connectée à une source d'agent lubrifiant par le biais d'une conduite de connexion (32, 33) s'étendant dans l'excentrique (15) et dans l'arbre d'entraînement (14), la rainure de lubrification (31) étant disposée de telle sorte qu'elle soit connectée au canal de connexion (34, 35) dans l'anneau de levage (12) lorsque ce canal de connexion (34, 35) est en liaison avec la chambre de décharge (22).
  14. Pompe haute pression selon l'une quelconque des revendications 1 à 13, caractérisée en ce qu'une rainure annulaire de collecte (28) ouverte vers le piston (6) est réalisée dans la paroi de l'alésage du cylindre (7), sert à recueillir le liquide de fuite qui traverse la fente entre la paroi de l'alésage du cylindre (7) et le piston (6) et est raccordée à l'une des conduites d'évacuation (30).
  15. Pompe haute pression selon la revendication 14, caractérisée en ce qu'un alésage transversal (29) conduisant de l'alésage longitudinal (24) dans le piston (6) à sa paroi extérieure est prévu dans le piston (6), débouche dans la rainure annulaire de collecte (28) et sert à évacuer le liquide de fuite qui traverse la fente entre la paroi de l'alésage longitudinal (24) et le piston de commande (25).
  16. Pompe haute pression selon l'une quelconque des revendications 1 à 15, caractérisée en ce que la pompe haute pression (1, 1') est conçue pour refouler du carburant, notamment du carburant diesel.
  17. Pompe haute pression selon l'une quelconque des revendications 1 à 16, caractérisée en ce que le piston (6) présente à son extrémité opposée à la chambre de travail (8) une partie de base (9) dans laquelle est réalisée la chambre de décharge (22).
  18. Pompe haute pression selon la revendication 17, caractérisée en ce que le diamètre de la chambre de décharge (22) est supérieur au diamètre du passage (23).
  19. Pompe haute pression selon la revendication 18, caractérisée en ce que le diamètre de la chambre de décharge (22) est supérieur au diamètre d'un alésage longitudinal (24) appartenant au passage (23).
  20. Pompe haute pression selon l'une quelconque des revendications 1 à 19, caractérisée en ce que le passage (23) a le même diamètre sur toute sa longueur.
EP03773421A 2003-02-11 2003-12-04 Pompe haute pression Expired - Lifetime EP1592887B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06026525.3A EP1760312B1 (fr) 2003-02-11 2003-12-04 Pompe haute pression

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH2022003 2003-02-11
CH202032003 2003-02-11
PCT/CH2003/000802 WO2004072477A1 (fr) 2003-02-11 2003-12-04 Pompe haute pression

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP06026525.3A Division EP1760312B1 (fr) 2003-02-11 2003-12-04 Pompe haute pression

Publications (2)

Publication Number Publication Date
EP1592887A1 EP1592887A1 (fr) 2005-11-09
EP1592887B1 true EP1592887B1 (fr) 2007-02-28

Family

ID=32855128

Family Applications (2)

Application Number Title Priority Date Filing Date
EP03773421A Expired - Lifetime EP1592887B1 (fr) 2003-02-11 2003-12-04 Pompe haute pression
EP06026525.3A Expired - Lifetime EP1760312B1 (fr) 2003-02-11 2003-12-04 Pompe haute pression

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP06026525.3A Expired - Lifetime EP1760312B1 (fr) 2003-02-11 2003-12-04 Pompe haute pression

Country Status (8)

Country Link
US (2) US7108491B2 (fr)
EP (2) EP1592887B1 (fr)
JP (1) JP2006514195A (fr)
CN (1) CN100392241C (fr)
AT (1) ATE355460T1 (fr)
AU (1) AU2003281906A1 (fr)
DE (1) DE50306704D1 (fr)
WO (1) WO2004072477A1 (fr)

Families Citing this family (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006514195A (ja) * 2003-02-11 2006-04-27 ガンサー−ハイドロマグ アーゲー 高圧ポンプ
ATE487057T1 (de) * 2004-02-25 2010-11-15 Ganser Hydromag Brennstoffeinspritzventil für verbrennungskraftmaschinen
US7134846B2 (en) * 2004-05-28 2006-11-14 Stanadyne Corporation Radial piston pump with eccentrically driven rolling actuation ring
WO2006037672A1 (fr) * 2004-10-06 2006-04-13 Siemens Aktiengesellschaft Pompe haute pression
US7278443B2 (en) 2004-12-16 2007-10-09 Diversified Dynamics Corporation Pulsation causing valve for a plural piston pump
US7290561B2 (en) 2004-12-16 2007-11-06 Diversified Dynamics Corporation Pulsation causing valve for a plural piston pump
US20060140778A1 (en) * 2004-12-28 2006-06-29 Warren Leslie J Reciprocating positive displacement pump for deionized water and method of cooling and lubricating therefor
FR2904665B1 (fr) * 2006-08-04 2008-10-31 Siemens Automotive Hydraulics Pompe transfert pour injection d'essence a haute pression
DE102007011192A1 (de) * 2007-03-06 2008-09-18 Perma-Tec Gmbh & Co. Kg Dosiervorrichtung für einen Schmierstoffspender
US8328538B2 (en) * 2007-07-11 2012-12-11 Gast Manufacturing, Inc., A Unit Of Idex Corporation Balanced dual rocking piston pumps
HUE026768T2 (en) * 2007-10-12 2016-07-28 Delphi Int Operations Luxembourg Sarl Fuel Pump Improvements
US8986253B2 (en) 2008-01-25 2015-03-24 Tandem Diabetes Care, Inc. Two chamber pumps and related methods
ITMI20080431A1 (it) * 2008-03-13 2009-09-14 Bosch Gmbh Robert Pompa di alta pressione per alimentare combustibile a un motore a combustione interna
DE102008001713A1 (de) * 2008-05-13 2009-11-19 Robert Bosch Gmbh Radialkolbenpumpe
US8182247B2 (en) * 2008-05-27 2012-05-22 Txam Pumps Llc Pump with stabilization component
US8408421B2 (en) 2008-09-16 2013-04-02 Tandem Diabetes Care, Inc. Flow regulating stopcocks and related methods
AU2009293019A1 (en) 2008-09-19 2010-03-25 Tandem Diabetes Care Inc. Solute concentration measurement device and related methods
WO2011014704A2 (fr) 2009-07-30 2011-02-03 Tandem Diabetes Care, Inc. Système de pompe de perfusion à cartouche jetable comprenant une décharge de pression et une rétroaction de pression
JP5633387B2 (ja) * 2011-01-24 2014-12-03 株式会社デンソー 燃料供給ポンプ
US9180242B2 (en) 2012-05-17 2015-11-10 Tandem Diabetes Care, Inc. Methods and devices for multiple fluid transfer
US9555186B2 (en) 2012-06-05 2017-01-31 Tandem Diabetes Care, Inc. Infusion pump system with disposable cartridge having pressure venting and pressure feedback
EP2711547B1 (fr) * 2012-09-24 2019-06-05 Continental Automotive GmbH Agencement de piston d'une pompe haute pression
DE102012024924A1 (de) 2012-12-19 2014-06-26 Volkswagen Aktiengesellschaft Vorrichtung zum Antrieb einer Kolbenpumpe
CN103967743A (zh) * 2013-01-29 2014-08-06 王彦彬 磁力式同平面多缸多级组合压缩机
CN103967745A (zh) * 2013-01-30 2014-08-06 王彦彬 同平面多缸多级凸轮组合压缩机
US9173998B2 (en) 2013-03-14 2015-11-03 Tandem Diabetes Care, Inc. System and method for detecting occlusions in an infusion pump
AU2016258571B2 (en) 2015-05-01 2020-01-30 Graco Minnesota Inc. Two piece pump rod
EP3601777B1 (fr) * 2017-03-29 2021-10-27 Wärtsilä Finland Oy Ensemble pompe à carburant haute pression pour moteur à piston à combustion interne
CN108457853B (zh) * 2018-04-10 2019-08-20 中国北方发动机研究所(天津) 一种高压泵柱塞自增压润滑结构
CN110332104B (zh) * 2019-08-14 2024-05-28 德帕姆(杭州)泵业科技有限公司 一种防咬死电动调量机构的计量泵
DE102020116294A1 (de) * 2020-06-19 2021-12-23 Hauhinco Maschinenfabrik G. Hausherr, Jochums Gmbh & Co. Kg Hubkolbenpumpe zum Fördern eines Mediums
CN115807748A (zh) * 2022-12-07 2023-03-17 北京天玛智控科技股份有限公司 柱塞滑靴组件和多边形轮盘驱动的径向柱塞泵

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3093301A (en) * 1960-07-05 1963-06-11 Mitchell Co John E Lubricating system for compressor
DE1653632A1 (de) * 1967-03-25 1971-09-16 Teves Gmbh Alfred Radialkolbenpumpe
US3456874A (en) * 1967-08-01 1969-07-22 Eaton Yale & Towne Cam driven compressor
US4132510A (en) * 1976-06-09 1979-01-02 Sampei Komiya Compressor
EP0520286B1 (fr) * 1991-06-27 1995-12-20 LuK Automobiltechnik GmbH & Co. KG Pompe à pistons radiaux
JPH06173811A (ja) * 1992-10-08 1994-06-21 Nippon Soken Inc 燃料噴射装置
DE4305791C2 (de) * 1993-02-25 2001-12-13 Hydraulik Ring Gmbh Radialkolbenpumpe, insbesondere Kraftstoffpumpe für Verbrennungsmotoren
JP2885133B2 (ja) * 1995-06-12 1999-04-19 トヨタ自動車株式会社 内燃機関のピストン
IT239879Y1 (it) * 1996-12-23 2001-03-13 Elasis Sistema Ricerca Fiat Perfezionamenti ad una pompa a pistoni, in particolare ad una pompa apistoni radiali per il carburante di un motore a combustione interna.
DE19705205A1 (de) * 1997-02-12 1998-08-13 Bosch Gmbh Robert Kolbenpumpe
DE19756727A1 (de) * 1997-11-07 1999-05-12 Itt Mfg Enterprises Inc Kolbenpumpe
DE19753593A1 (de) * 1997-12-03 1999-06-17 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
DE19906626A1 (de) * 1998-10-06 2000-04-13 Mannesmann Rexroth Ag Pumpenanordnung
US6183212B1 (en) 1999-02-17 2001-02-06 Stanadyne Automotive Corp. Snap-in connection for pumping plunger sliding shoes
WO2002097268A1 (fr) * 2001-05-26 2002-12-05 Robert Bosch Gmbh Pompe haute pression pour un systeme de carburant d'un moteur a combustion interne
DE10213625A1 (de) * 2001-05-26 2002-12-05 Bosch Gmbh Robert Kolbenpumpe, insbesondere Hochdruckpumpe für ein Kraftstoffsystem einer Brennkraftmaschine, sowie Kraftstoffsystem und Brennkraftmaschine
JP2003074439A (ja) * 2001-06-19 2003-03-12 Denso Corp 燃料噴射ポンプ
WO2003014569A1 (fr) 2001-08-08 2003-02-20 Crt Common Rail Technologies Ag Pompe d'alimentation haute pression
DE10345406A1 (de) 2002-10-14 2004-04-22 Crt Common Rail Technologies Ag Hochdruckpumpe, insbesondere für ein Common-Rail-Einspritzsystem
JP2006514195A (ja) * 2003-02-11 2006-04-27 ガンサー−ハイドロマグ アーゲー 高圧ポンプ
DE10330757A1 (de) * 2003-07-07 2005-02-03 Bernhard-Rudolf Frey Exzentertriebwerk für volumetrisch wirkende Pumpen oder Motoren

Also Published As

Publication number Publication date
US20060062677A1 (en) 2006-03-23
EP1760312A3 (fr) 2007-09-05
CN1748083A (zh) 2006-03-15
US20060275164A1 (en) 2006-12-07
US7108491B2 (en) 2006-09-19
EP1592887A1 (fr) 2005-11-09
ATE355460T1 (de) 2006-03-15
AU2003281906A1 (en) 2004-09-06
EP1760312B1 (fr) 2013-05-01
WO2004072477A1 (fr) 2004-08-26
EP1760312A2 (fr) 2007-03-07
CN100392241C (zh) 2008-06-04
DE50306704D1 (de) 2007-04-12
JP2006514195A (ja) 2006-04-27

Similar Documents

Publication Publication Date Title
EP1592887B1 (fr) Pompe haute pression
EP2049794B1 (fr) Dispositif d'étancheité et de guidage pour un piston d'une pompe à piston
EP0547404A1 (fr) Pompe à membrane actionnée hydrauliquement avec limitation du mouvement de la membrane
DE2503346A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE69724695T2 (de) Radialkolbenpumpe
EP2483558A1 (fr) Pompe pour un appareil de nettoyage à haute pression
DE1576281A1 (de) Kraftstoffeinspritzpumpe fuer Brennkraftmaschinen
DE10139055A1 (de) Verfahren, Computerprogramm, Steuer- und/oder Regelgerät sowie Kraftstoffsystem für eine Brennkraftmaschine
EP0400693A2 (fr) Pompe à haute pression
DE2419460A1 (de) Einrichtung zur regelung einer pumpe
DE102008009195A1 (de) Vorrichtung zum Aufkonzentrieren einer Flüssigkeit mittels einer Differentialkolbenpumpe
EP1998045A1 (fr) Machine volumétrique avec soupapes coaxiales
CH652805A5 (de) Druckumsetzer mit mindestens drei oelhydraulisch angetriebenen kolben.
DE3928411C2 (fr)
DE4315646A1 (de) Kraftstoffeinspritzpumpe für Brennkraftmaschinen
WO2008124950A1 (fr) Machine de refoulement construite selon le principe de la spirale
DE3001570C2 (de) Einrichtung zur Mengenregulierung für die von einer Mehrkolbenhochdruckpumpe eines Hochdruckreinigers abgegebene Flüssigkeitsmenge
DE2841083C2 (fr)
DE2521367A1 (de) Hydraulische anlage
DE2318915C2 (de) Folgesteuereinrichtung für eine einseitig verstellbare hydrostatische Verdrängermaschine
EP1798415B1 (fr) Pompe à haute pression
DE2218391A1 (de) Radialkolbenpumpe
DE1040375B (de) Pumpe mit pulsierender Arbeitsweise
EP1022461A2 (fr) Pompe haute pression
DE10205495A1 (de) Kraftstoffpumpe, insbesondere für Brennkraftmaschinen mit Kraftstoff-Direkteinspritzung

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: 20050801

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

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: 20070228

Ref country code: IE

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: 20070228

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: 20070228

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: 20070228

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20070228

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: PATENTANWAELTE SCHAAD, BALASS, MENZL & PARTNER AG

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 50306704

Country of ref document: DE

Date of ref document: 20070412

Kind code of ref document: P

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

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 EXPIRATION OF PROTECTION

Effective date: 20070529

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

Ref country code: SE

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: 20070531

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

Ref country code: ES

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: 20070608

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: 20070730

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

EN Fr: translation not filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20070228

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

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: 20070228

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: 20070228

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

26N No opposition filed

Effective date: 20071129

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

Ref country code: IT

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: 20070228

Ref country code: FR

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: 20071019

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: 20070529

BERE Be: lapsed

Owner name: GANSER-HYDROMAG AG

Effective date: 20071231

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 NON-PAYMENT OF DUE FEES

Effective date: 20071231

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: 20071231

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

Ref country code: FR

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: 20070228

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: 20070228

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

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: 20070228

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: 20071204

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

Effective date: 20070901

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: 20070228

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 50306704

Country of ref document: DE

Representative=s name: KOTITSCHKE & HEURUNG PARTNERSCHAFT MBB PATENT-, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 50306704

Country of ref document: DE

Representative=s name: KOTITSCHKE & HEURUNG PARTNERSCHAFT, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 50306704

Country of ref document: DE

Representative=s name: KOTITSCHKE & HEURUNG PARTNERSCHAFT MBB, DE

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

Ref country code: DE

Payment date: 20131220

Year of fee payment: 11

Ref country code: AT

Payment date: 20131211

Year of fee payment: 11

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

Ref country code: FI

Payment date: 20131211

Year of fee payment: 11

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50306704

Country of ref document: DE

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

Ref country code: FI

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

Effective date: 20141204

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 355460

Country of ref document: AT

Kind code of ref document: T

Effective date: 20141204

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

Ref country code: DE

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

Effective date: 20150701

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 NON-PAYMENT OF DUE FEES

Effective date: 20141204

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

Ref country code: CH

Payment date: 20161221

Year of fee payment: 14

Ref country code: GB

Payment date: 20161222

Year of fee payment: 14

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20171204

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

Ref country code: GB

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

Effective date: 20171204

Ref country code: CH

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

Effective date: 20171231

Ref country code: LI

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

Effective date: 20171231