EP2423498A1 - Soupape de limitation de débit passive - Google Patents

Soupape de limitation de débit passive Download PDF

Info

Publication number
EP2423498A1
EP2423498A1 EP11169400A EP11169400A EP2423498A1 EP 2423498 A1 EP2423498 A1 EP 2423498A1 EP 11169400 A EP11169400 A EP 11169400A EP 11169400 A EP11169400 A EP 11169400A EP 2423498 A1 EP2423498 A1 EP 2423498A1
Authority
EP
European Patent Office
Prior art keywords
valve
input
closing element
piston
quantity limiting
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.)
Granted
Application number
EP11169400A
Other languages
German (de)
English (en)
Other versions
EP2423498B1 (fr
Inventor
Andreas Carelli
Kees Kuipers
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.)
Wartsila NSD Schweiz AG
Original Assignee
Wartsila NSD Schweiz 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 Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP11169400.6A priority Critical patent/EP2423498B1/fr
Publication of EP2423498A1 publication Critical patent/EP2423498A1/fr
Application granted granted Critical
Publication of EP2423498B1 publication Critical patent/EP2423498B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0205—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
    • F02M63/0215—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits

Definitions

  • the invention relates to a passive flow control valve for a large diesel engine according to the preamble of the independent claim of this category.
  • the invention further relates to a large diesel engine with such a flow control valve.
  • the common rail system has become established for fuel supply.
  • the fuel is conveyed by means of a high pressure pump in a pressure accumulator, which is also referred to as an accumulator or as a rail.
  • a pressure accumulator is fuel at a pressure of for example 1600 bar or more, z. B. up to 2000 bar.
  • the fuel injectors of all cylinders are supplied, which inject the fuel into the respective cylinder. It is known to provide between the accumulator and each fuel injector each a passive flow control valve.
  • a problem known quantity limiting valves in the large diesel engine results from the viscosity fluctuations of the fuel, which are particularly temperature-related.
  • heavy fuel is usually used as fuel, which typically has to be heated to temperatures above 100 ° C due to its very high viscosity in order to be sufficiently flowable or even injectable.
  • significantly lower-viscosity marine diesel oil is used, with which usually the engine is started and also switched off.
  • the engine is operated with marine diesel oil and then continuously transferred to the heavy oil operation on the open sea.
  • the operation with marine diesel oil is usually done at lower temperatures in the fuel supply system than the operation with heavy oil.
  • the present invention seeks to remedy this undesirable effect. Accordingly, it is an object of the invention to propose a passive flow control valve for a large diesel engine, in which the amount, after passing the valve closes automatically, is substantially independent of the viscosity of the medium.
  • a passive flow control valve for a large diesel engine with a valve housing having an inlet and an outlet for a flowable medium and a valve chamber arranged therebetween, wherein in the valve chamber, a valve body is provided with an input-side and an output-side closing element, respectively designed for sealing cooperation with an input-side and an output-side Ventisitz, wherein the input-side closing element is biased by a spring against the input-side valve seat, and provided with a valve body piston, the outside of which is slidably guided through the wall of the valve chamber.
  • In the front of the Piston is provided at least one passage bore through which the flowable medium can flow.
  • the piston divides the valve chamber into a front chamber and a rear chamber, wherein the at least one passage bore in the end face of the piston forms a flow connection between the rear chamber and the front chamber.
  • Quantity limiting valve when the input-side closing element is designed for line contact with the input-side valve seat.
  • the output-side closing element is designed for line contact with the output-side valve seat.
  • the line contact can in particular be rationalized by the fact that the input-side closing element or the output-side closing element have a spherical surface for interacting with the input-side and the output-side valve seat.
  • the center of curvature of the spherical surface is eccentric with respect to the longitudinal axis of the valve body. This makes it possible to realize a smaller curvature of the spherical surface, which increases the length of the line contact. As a result, the opening pressure, or more precisely the pressure difference required for opening, can be set to small values.
  • the input-side valve seat or the output-side valve seat have a conical surface. This can be achieved particularly good sealing effects.
  • the input-side closing element and the output-side closing element are designed the same.
  • valve body extends inside the spring. This is a structurally particularly simple embodiment.
  • each passage bore is arranged outside the spring with respect to the radial direction.
  • the pressure difference for opening the flow connection between the input-side valve seat and the input-side closing element is 2 bar to 20 bar. This is due to the fact that the flow control valve should remain in the closed state, when circulating the fuel between the reservoir and the pressure accumulator is circulated. Usually amounts the pressure in the accumulator during recirculation between 2 and 20 bar, for example 10 bar. Then, the pressure difference for opening the flow connection between the input-side valve seat and the input-side closing element is set slightly higher, for example to 15 bar, so that no opening results in the circulation operation.
  • the piston is designed as a separate part and is connected to the valve body.
  • the spring is supported on the end face of the piston.
  • the invention further proposes a large diesel engine with an inventive quantity limiting valve.
  • the quantity limiting valve is preferably arranged between a high-pressure accumulator for the fuel and a fuel injection nozzle.
  • Fig. 1 shows a longitudinal sectional view of an embodiment of an inventive Mengenbegrenzungsventils, which is designated overall by the reference numeral 1. The cut takes place along the longitudinal axis A of the quantity limiting valve 1.
  • the quantity limiting valve 1 is a passive valve, which means that it is not activated or actuated actively, for example by a control signal, but independently and automatically opens and closes depending on the prevailing pressure differences.
  • the passive flow control valve 1 has a valve housing 2, which is configured here in two parts, and a lower part 21 and a cover or upper part 22 includes. The upper part 22 and the lower part 21 are connected by means of several screws 23 firmly together.
  • the valve housing 2 has an inlet 3 and an outlet 4 for a flowable medium. Between the inlet 3 and the outlet 4, a valve chamber 5 is provided in the valve housing 2, in which a valve body 6 is arranged, which extends in the direction of the longitudinal axis A.
  • FIG. 3 another illustration of the valve body 6. Its two axial ends are formed by two closing elements 63, 64, namely the input side Closing element 63 and the output-side closing element 64. These closing elements 63, 64 are designed for sealing cooperation with an input-side valve seat 31 and an output-side valve seat 41.
  • Both valve seats 31, 41 are provided in the valve housing 2, namely at the input end of the valve chamber 5 and at the output end of the valve chamber 5.
  • the valve seats 31, 41 can be incorporated directly into the valve housing 2, or they are made as separate parts, the then inserted into corresponding recesses in the valve housing 2 and fixed there, for example by shrinking. Depending on the application, it may be more advantageous to make the valve seats 31, 41 as separate parts, because this results in a higher flexibility with respect to the material. Because the valve seats 31, 41 can then be made of a different material than the valve housing. 2
  • both the input-side valve seat 31 and the output-side valve seat 41 each have a conical surface 32 and 42, which cooperate with the input-side closing element 63 and with the output-side closing element 64.
  • a piston 7 is provided, which is dimensioned with respect to its outer diameter so that the outer side is slidably guided through the wall of the valve chamber 5. Between the outside of the piston 7 and the wall of the valve chamber 5, a slight clearance is provided.
  • Fig. 4 a representation of the valve body 6 with the piston 7.
  • the piston 7 is designed substantially cylindrical and arranged so that its cylinder axis coincides with the longitudinal axis A.
  • the piston 7 has on its side facing the inlet 3 an end face 71, the other axial end of the piston 7 is open.
  • valve body 6 and the piston 7 may be configured in one piece. Manufacturing technology, however, it is usually cheaper to make the valve body 6 and the piston 7 as two separate components and then connect them.
  • the piston 7 can also be made of more than one part, for example of different materials, to optimally adapt its properties to the particular application or to simplify the production.
  • the end face 71 of the piston 7 is provided with a central recess 72 which serves to receive the valve body 6.
  • the valve body 6 has a flange-like projection 65, which serves as a stop for the end face 71.
  • the valve body 6 is pushed from the inside through the central recess 72 in the end face 71 until the flange-like projection 65 bears against the end face 71 from the inside.
  • the dimensions are coordinated so that the input-side closing element 63 of the valve body 6 extends completely beyond the end face 71 of the piston 7 (see Fig. 4 ).
  • the piston 7 is shrunk onto the valve body 6.
  • At least one passage bore 73 is provided in the end face 71 of the piston, which extends in the axial direction parallel to the longitudinal axis A through the end face 71.
  • a plurality of passage bores 73 are provided.
  • Each passage bore 73 has a diameter d and a length L, wherein the diameter d is the diameter which is decisive for the flow resistance, that is to say generally the smallest diameter of the passage bore 73.
  • a plurality of bores 74 are also provided, which each extend in the radial direction through the wall of the piston 7.
  • the radial direction is meant the direction perpendicular to the axial direction, wherein the axial direction is determined by the longitudinal axis A.
  • the holes 74 Through the holes 74, the flowable medium can escape and reach the wall of the valve chamber 5, to provide here, for example, for a lubrication of the piston 7.
  • valve body 6 is biased together with the piston 7 by means of a spring 8 against the input-side valve seat 31, so that the input-side closing element 63 is pressed against the input-side valve seat 31.
  • the spring 8 extends in the axial direction and coaxial with the valve body 6, so that the valve body 6 extends in the interior of the spring 8.
  • the spring 8 is supported on the one hand on the valve housing 2, namely around the output-side valve seat 41 around, and on the other hand inside on the end face of the piston. 7
  • the quantity limiting valve 1 is suitable for the common rail system of a large diesel engine.
  • a large diesel engine In modern large diesel engines, there are usually several common rail systems, for example for fuel injection, gas exchange or auxiliary systems.
  • fuel injection Large diesel engines are usually operated with heavy fuel oil, which means that the flowable medium is heavy oil in this case.
  • marine diesel oil is used, which is used in particular for engine operation in the port, that is, before the ship leaves the port or when it enters the harbor area, the large diesel engine is typically operated with marine diesel.
  • the operating temperature of the fuel is when operating with diesel fuel usually much lower than in heavy oil operation. This also results in fluctuations in the viscosity of the fuel.
  • the inventive flow control valve 1 is heavy oil suitable and can therefore be used in the common rail system of the fuel injection of a large diesel engine.
  • Fig. 2 shows a schematic representation of such a common rail system of a large diesel engine.
  • the system comprises a high pressure pump 50, with which the fuel, namely the heavy oil, is conveyed into a pressure accumulator 51, which is also referred to as an accumulator or as a rail.
  • This pressure accumulator 51 is usually designed as a tube-like component which extends approximately at the level of the cylinder heads along the engine. From the pressure accumulator branch off lines 52 which lead to the fuel injection nozzles 53 in order to supply them with heavy oil. In Fig. 2 only one such conduit 52 and only one fuel injector 53 is shown because it is sufficient for understanding.
  • the heavy oil is under a pressure which substantially corresponds to the injection pressure.
  • This pressure is 1600 bar, for example, but may even be higher, for example up to 2000 bar.
  • the flow limiting valve 1 is provided, which is for example mounted directly on or on the pressure accumulator 51.
  • the quantity limiting valve 1 is arranged so that its inlet 3 is in fluid communication with the pressure accumulator 51 and its outlet 4 with the line 52nd
  • the quantity limiting valve 1 is in the in Fig. 1 illustrated closing position in which the input-side closing element 63 sealingly cooperates with the input-side valve seat 31 so that no heavy oil can flow through the flow control valve 1. In this condition prevails at the outlet 4 and on Inlet 3, substantially the same fluid pressure through the heavy oil.
  • the spring 8 presses the input-side closing element 63 sealingly into the input-side valve seat 31.
  • the pressure in the conduit 52 drops. This has the consequence that the valve body 6 with the piston 7 Justicesgeffless ( Fig. 1 ) is moved upward, whereby the input-side closing element 63 is lifted out of the input-side valve seat 31, so that the heavy oil from the pressure accumulator 51 pass through the passage holes 73, the quantity limiting valve 1 and can flow into the conduit 52.
  • the pressure difference required to open the flow connection at the input side valve seat 31 can be adjusted by various measures, which will be explained later.
  • this pressure difference is set to a value of 2 bar to 20 bar.
  • the pressure difference is set to a value which is greater than the pressure in the pressure accumulator 51 during the circulation operation.
  • the stroke of the piston 7 is dependent and at least approximately proportional to the amount of the injected amount of heavy oil.
  • the piston 7 reaches its maximum stroke when the maximum amount of heavy oil has flowed through the flow restrictor valve 1.
  • the quantity limiting valve 1 is dimensioned or designed so that in a regular or normal injection process, the maximum stroke of the piston 7 is not sufficient to press the output-side closing element 64 sealingly in the output-side valve seat 41.
  • the large diesel engine is switched off. So that the fuel does not cool and becomes so heavy or almost solid that it clogs the fuel supply system, it is customary in a circulation operation, the fuel from the reservoir through the pressure accumulator 51 and by an in Fig. 2 not shown return flow line to circulate back into the reservoir.
  • This circulation operation usually takes place only with backing pumps, not shown, that is, the high-pressure pump 50 is not active in this circulation operation.
  • the pressure in the pressure accumulator 51 in the circulation operation is 2 bar to 20 bar, for example 10 bar.
  • the pressure difference for opening the flow connection between the input-side valve seat 31 and the input-side closing element 63 is set to a value of 2 bar to 20 bar, namely to a value , which is greater than the pressure in the pressure accumulator 51 during the circulation operation.
  • a pressure difference of 2 bar to 20 bar means that the input-side closing element 63 opens only when the pressure at the representation according to ( Fig. 1 ) Underside of the end face 71 is smaller by this value between 2 and 20 bar than the pressure at the inlet 3 of the quantity limiting valve 1.
  • An essential aspect of the inventive quantity limiting valve 1 is that the at least one passage bore 73 is provided in the end face 71 of the piston 7.
  • each passage bore 73 through which the fuel flows (or is pushed back) can be kept very short, whereby the hydrodynamic flow resistance of the passage bore 73 is independent of the viscosity of the fuel.
  • This independence of viscosity means that a very accurate and consistent limitation of the fuel quantity can be realized to a certain value, this value being subject to no changes even in the case of viscosity fluctuations.
  • the hydrodynamic flow resistance of the passage bore is independent of the viscosity of the medium flowing through, it has proved to be particularly advantageous if the ratio of the length L of the passage bore 73 to the diameter d of the passage bore 73 is at most 4.
  • diameter d is meant the diameter d which is decisive for the flow resistance, which in the case of a diameter varying over the length L is generally the minimum or the smallest diameter.
  • the operating pressure in the accumulator 51 is very large, for example, 1600 bar or up to 2000 bar, it is of course very important that a very good sealing effect between the input-side valve seat 31 and the input-side closing element 63 and between the output-side valve seat 41 and the output side closing element 64 is achieved.
  • the input-side closing element 63 or the output-side closing element 64 and in particular both closing elements 63, 64 are designed for line contact with the input-side valve seat 31 and the output-side valve seat 41. Such a line contact between the involved partners is very efficient and in particular leak-free.
  • the line contact is very tolerant of tilting of the piston 7, ie even with slight tilting or misalignment of the piston 7, the high sealing effect is ensured.
  • the line contact is realized both at the input-side valve seat 31 and at the output-side valve seat 41, that the input-side closing element 63 and the output-side closing element 64 each have a spherical surface 631 and 641 for cooperation with the respective conical surface 32 and 42 of the input-side and the output-side valve seat 31, 41 have.
  • the position of the line contact with respect to the axial direction influences the pressure difference necessary for opening the respective flow connection.
  • the length of the line contact which is measured over the entire circumference, is the higher the higher-with respect to the illustration in FIG Fig. 1 -
  • the line contact with respect to the axial direction is ..
  • the greater the length of the line contact the lower the pressure difference, which is required to open the flow connection.
  • the pressure difference can be set via the position of the line contact of the spherical surface 631 or 641, in which the respective flow connection is opened.
  • the center of curvature M of the spherical surface 631 or, respectively, 641 is eccentric with respect to the longitudinal axis A of the valve body 6.
  • the center of curvature M here as the center of the sphere on whose surface the spherical surface 631 or 641 is located, lies on a straight line K that lies parallel to the longitudinal axis A and has a distance e from the longitudinal axis A.
  • the curvature is relatively small in terms of practical feasibility, but it should advantageously be so large as to ensure line contact between the surfaces 631 and 641 and the conical surfaces 32 and 42, respectively.
  • the length of the respective line contact - and thus the pressure difference required for opening can be adjusted for a given curvature over the size of the distance e.
  • Another measure with which the pressure difference for opening the respective flow connection can be influenced or adjusted is the choice of the elastic properties, especially the choice of the spring constants, of the spring 8.
  • Another advantageous measure is when the input-side closing element 63 and the output-side closing element 64, at least with respect to the surface, which cooperates with the respective valve seat 31, 41, are designed the same. By this symmetry, a self-centering effect of the valve body 6 can be realized. Due to the slight play between the lateral surface of the piston 7 and the wall of the valve chamber 5, a simple centering of the valve body 6 is achieved.
  • a line contact between the input-side closing element 63 and the input-side valve seat 31 or between the output-side closing element 64 and the output-side valve seat 41 can also be realized by other geometric configurations of the respective interacting surfaces.
  • both cooperating surfaces may each be configured as spherical surfaces, or both interacting surfaces are each configured as conical surfaces, in particular with different cone angles.
  • all the passage bores 73 are preferably outside the spring 8 with respect to the axial direction, that is to say the distance between the center axis of the passage bore 73 and the longitudinal axis A is greater than half the outside diameter of the spring 8 plus the radius of the respective bore 73 for each passage bore on the outer surface of the end face 71 of the piston.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Safety Valves (AREA)
EP11169400.6A 2010-08-26 2011-06-10 Soupape de limitation de débit passive Not-in-force EP2423498B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP11169400.6A EP2423498B1 (fr) 2010-08-26 2011-06-10 Soupape de limitation de débit passive

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP10174196 2010-08-26
EP11169400.6A EP2423498B1 (fr) 2010-08-26 2011-06-10 Soupape de limitation de débit passive

Publications (2)

Publication Number Publication Date
EP2423498A1 true EP2423498A1 (fr) 2012-02-29
EP2423498B1 EP2423498B1 (fr) 2013-09-11

Family

ID=43085844

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11169400.6A Not-in-force EP2423498B1 (fr) 2010-08-26 2011-06-10 Soupape de limitation de débit passive

Country Status (5)

Country Link
EP (1) EP2423498B1 (fr)
JP (1) JP5881981B2 (fr)
KR (1) KR101917389B1 (fr)
CN (1) CN102383995B (fr)
DK (1) DK2423498T3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT513158A1 (de) * 2012-04-10 2014-02-15 Bosch Gmbh Robert Durchflussbegrenzer mit Kugel und Drossel
DE102014105439A1 (de) 2014-04-16 2015-10-22 L'orange Gmbh Mengenbegrenzungsventil, insbesondere für ein Dual-Fuel-Kraftstoffeinspritzsystem
WO2015177399A1 (fr) * 2014-05-22 2015-11-26 Wärtsilä Finland Oy Élément de raccordement
EP3023628A1 (fr) 2014-11-21 2016-05-25 O.M.T. Officine Meccaniche Torino S.p.A. Soupape de limitation de débit de carburant pour moteurs à combustion interne de grande taille
DE102016101425A1 (de) 2016-01-27 2017-07-27 Firma L'orange Gmbh Mengenbegrenzungsventil, insbesondere für ein Hochdruckpumpensystem

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103016426B (zh) * 2012-12-06 2016-01-20 联合汽车电子有限公司 集成有泄压阀的喷射泵喷嘴
DE102013210983B4 (de) * 2013-06-12 2021-04-29 Mtu Friedrichshafen Gmbh Mengenbegrenzungsventil

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002077441A1 (fr) * 2001-03-22 2002-10-03 Mtu Friedrichshafen Gmbh Procede pour injecter du carburant dans les chambres de combustion d'un moteur a combustion interne et systeme d'injection de carburant destine a un tel moteur
EP1270931A2 (fr) * 2001-06-27 2003-01-02 Wärtsilä Technology Oy AB Vanne de coupure de combustible
WO2004111440A1 (fr) * 2003-06-17 2004-12-23 Wärtsilä Finland Oy Agencement dans un appareil d'alimentation en carburant
DE102005012165A1 (de) * 2005-03-17 2006-09-28 L'orange Gmbh Kraftstoffspeicher eines Kraftstoffeinspritzsystems für mehrzylindrige Brennkraftmaschinen und Mengenbegrenzungsventil für einen solchen
DE102005036780A1 (de) * 2005-08-02 2007-02-08 L'orange Gmbh Kraftstoff-Einspritzsystem für eine Brennkraftmaschine
EP1988279A1 (fr) * 2007-05-03 2008-11-05 L'Orange Gmbh Système d'injection pour moteurs à combustion interne fonctionnant au carburant, en particulier à l'huile lourde

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES445020A1 (es) * 1976-02-10 1977-06-01 Bendiberica Sa Perfeccionamientos en valvulas de limitacion de presion.
JP2943340B2 (ja) * 1991-01-24 1999-08-30 株式会社デンソー 蓄圧式燃料噴射装置
DE4414242A1 (de) * 1994-04-23 1995-10-26 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE19548610A1 (de) * 1995-12-23 1997-06-26 Bosch Gmbh Robert Kraftstoffeinspritzeinirchtung für Brennkraftmaschinen
JP3918253B2 (ja) * 1997-09-10 2007-05-23 三菱ふそうトラック・バス株式会社 蓄圧式燃料噴射装置の安全装置
JPH11280930A (ja) * 1998-03-30 1999-10-15 Denso Corp ガス抜き弁
DE19822671A1 (de) * 1998-05-20 1999-11-25 Bosch Gmbh Robert Druckbegrenzungsventil
JP3555588B2 (ja) * 2001-03-23 2004-08-18 トヨタ自動車株式会社 コモンレール式燃料噴射装置
FI117643B (fi) * 2003-01-15 2006-12-29 Waertsilae Finland Oy Järjestely polttoaineen syöttölaitteistossa
DE102004037419B3 (de) * 2004-07-30 2006-02-16 Siemens Ag Ventil für den Einsatz in einer kraftstoffführenden Leitung eines Kraftfahrzeuges
CN101223352B (zh) * 2005-07-18 2010-12-08 甘瑟-许德罗玛格股份公司 用于内燃机的蓄压式喷射***
JP4335280B2 (ja) * 2006-11-27 2009-09-30 三菱電機株式会社 燃料噴射弁

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002077441A1 (fr) * 2001-03-22 2002-10-03 Mtu Friedrichshafen Gmbh Procede pour injecter du carburant dans les chambres de combustion d'un moteur a combustion interne et systeme d'injection de carburant destine a un tel moteur
EP1270931A2 (fr) * 2001-06-27 2003-01-02 Wärtsilä Technology Oy AB Vanne de coupure de combustible
WO2004111440A1 (fr) * 2003-06-17 2004-12-23 Wärtsilä Finland Oy Agencement dans un appareil d'alimentation en carburant
DE102005012165A1 (de) * 2005-03-17 2006-09-28 L'orange Gmbh Kraftstoffspeicher eines Kraftstoffeinspritzsystems für mehrzylindrige Brennkraftmaschinen und Mengenbegrenzungsventil für einen solchen
DE102005036780A1 (de) * 2005-08-02 2007-02-08 L'orange Gmbh Kraftstoff-Einspritzsystem für eine Brennkraftmaschine
EP1988279A1 (fr) * 2007-05-03 2008-11-05 L'Orange Gmbh Système d'injection pour moteurs à combustion interne fonctionnant au carburant, en particulier à l'huile lourde

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT513158A1 (de) * 2012-04-10 2014-02-15 Bosch Gmbh Robert Durchflussbegrenzer mit Kugel und Drossel
AT513158B1 (de) * 2012-04-10 2014-03-15 Bosch Gmbh Robert Durchflussbegrenzer mit Kugel und Drossel
DE102014105439A1 (de) 2014-04-16 2015-10-22 L'orange Gmbh Mengenbegrenzungsventil, insbesondere für ein Dual-Fuel-Kraftstoffeinspritzsystem
WO2015158413A1 (fr) 2014-04-16 2015-10-22 L'orange Gmbh Valve de limitation de débit notamment destinée à un système d'injection de carburant en bicarburant
US10480467B2 (en) 2014-04-16 2019-11-19 L'orange Gmbh Flow limiting valve, in particular for a dual fuel injection system
WO2015177399A1 (fr) * 2014-05-22 2015-11-26 Wärtsilä Finland Oy Élément de raccordement
EP3023628A1 (fr) 2014-11-21 2016-05-25 O.M.T. Officine Meccaniche Torino S.p.A. Soupape de limitation de débit de carburant pour moteurs à combustion interne de grande taille
DE102016101425A1 (de) 2016-01-27 2017-07-27 Firma L'orange Gmbh Mengenbegrenzungsventil, insbesondere für ein Hochdruckpumpensystem
DE102016101425B4 (de) 2016-01-27 2018-05-09 Firma L'orange Gmbh Mengenbegrenzungsventil, insbesondere für ein Hochdruckpumpensystem

Also Published As

Publication number Publication date
CN102383995A (zh) 2012-03-21
KR20120020056A (ko) 2012-03-07
KR101917389B1 (ko) 2018-11-09
JP2012047170A (ja) 2012-03-08
DK2423498T3 (da) 2013-12-09
EP2423498B1 (fr) 2013-09-11
CN102383995B (zh) 2016-04-27
JP5881981B2 (ja) 2016-03-09

Similar Documents

Publication Publication Date Title
EP2423498B1 (fr) Soupape de limitation de débit passive
EP0657642B1 (fr) Dispositif d'injection de combustible pour moteurs à combustion interne
EP2108080B1 (fr) Injecteur pour injecter du carburant dans les chambres de combustion des moteurs à combustion interne
DE112011102555T5 (de) Treibstoffsystem für große Zylinderbohrungen und Treibstoffinjektor für dasselbe
DE102007021330A1 (de) Kraftstoffinjektor für eine Brennkraftmaschine mit Common-Rail-Einspritzsystem
EP2852754B1 (fr) Injecteur d'un système d'injection de carburant
DE4341545A1 (de) Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE4320620B4 (de) Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE602004002686T2 (de) Kraftstoffinjektor mit kraftausgeglichenem Steuerventil
DE102009000181A1 (de) Kraftstoff-Injektor
AT511252B1 (de) Spülventil für common-rail schweröl- einspritzsysteme
EP2743493B1 (fr) Injecteur de carburant
EP1356203B1 (fr) Dispositif pour alimenter un moteur a combustion interne en carburant sous haute pression
DE102006026877A1 (de) Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine
EP2836696B1 (fr) Injecteur d'un système d'injection de carburant modulaire à rampe commune, doté d'un limiteur de débit
EP2439397A2 (fr) Injecteur de carburant
EP2511514B1 (fr) Soupape d'injection de combustible
DE3009750C2 (de) Brennstoffeinspritzvorrichtung für Brennkraftmaschinen
EP0995903B1 (fr) Dispositif d'injection de liquide dans un cylindre d' un moteur Diesel et moteur Diesel
WO2013117979A1 (fr) Dispositif d'injection de carburant dans la chambre de combustion d'un moteur à combustion interne
DE102016015038B4 (de) Kraftstoffinjektor
DE10209527A1 (de) Einrichtung zur druckmodulierten Formung des Einspritzverlaufes
EP2798192B1 (fr) Injecteur de carburant pour moteur à combustion
DE102018200565A1 (de) Injektor zur Dosierung von gasförmigem Kraftstoff, Gaseinblassystem mit einem solchen Injektor und Verfahren zum Betreiben dieses Injektors
AT511731B1 (de) Kavitationsoptimierte drosselbohrungen

Legal Events

Date Code Title Description
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

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: 20120829

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: F02M 63/00 20060101ALI20130301BHEP

Ipc: F02M 55/02 20060101ALI20130301BHEP

Ipc: F02M 63/02 20060101AFI20130301BHEP

INTG Intention to grant announced

Effective date: 20130409

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

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 631786

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130915

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502011001314

Country of ref document: DE

Effective date: 20131107

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

Effective date: 20131204

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

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: 20130911

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: 20130814

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: 20130911

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: 20130911

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: 20131211

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20130911

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: 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: 20130911

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: 20130911

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: 20131212

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: 20130911

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: 20130911

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

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: 20130911

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: 20130911

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: 20130911

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: 20140111

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: 20130911

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: 20130911

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

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: 20130911

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: 20130911

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011001314

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: 20140113

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: 20140612

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: 20130911

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011001314

Country of ref document: DE

Effective date: 20140612

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140610

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: 20130911

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20150227

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

Ref country code: LI

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

Effective date: 20140630

Ref country code: IE

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

Effective date: 20140610

Ref country code: CH

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

Effective date: 20140630

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 NON-PAYMENT OF DUE FEES

Effective date: 20140630

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

Effective date: 20150610

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: 20130911

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

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: 20130911

Ref country code: GB

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

Effective date: 20150610

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

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: 20130911

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: 20130911

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: 20110610

Ref country code: BE

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: 20140630

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: 20130911

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 631786

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160610

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: 20160610

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

Ref country code: MK

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: 20130911

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

Ref country code: DE

Payment date: 20180625

Year of fee payment: 8

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

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: 20130911

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

Ref country code: DK

Payment date: 20180620

Year of fee payment: 8

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502011001314

Country of ref document: DE

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

Effective date: 20190630

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: 20200101

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 NON-PAYMENT OF DUE FEES

Effective date: 20190630