EP3008327A1 - Quantity-limiting valve - Google Patents
Quantity-limiting valveInfo
- Publication number
- EP3008327A1 EP3008327A1 EP14729857.4A EP14729857A EP3008327A1 EP 3008327 A1 EP3008327 A1 EP 3008327A1 EP 14729857 A EP14729857 A EP 14729857A EP 3008327 A1 EP3008327 A1 EP 3008327A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- region
- face
- stop
- limiting valve
- 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
Links
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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/042—The valves being provided with fuel passages
-
- 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
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0077—Valve seat details
-
- 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
-
- 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
- F02M2200/28—Details of throttles in fuel-injection apparatus
Definitions
- the invention relates to a quantity limiting valve for an injection system
- a quantity limiting valve is provided to maximize the duration of the injector during one
- Internal combustion engine can be prevented by an excessive amount of injected fuel, for example, when the injector has a defect, so that it no longer or not completely closes.
- a flow control valve usually has one
- Inflow and an outflow on It also comprises a piston which is displaceably guided in a cylinder. By the piston, the inflow of the
- Quantity limiting valve is - as seen in the flow direction - arranged between the high-pressure source and the injector or integrated upstream of an actual injection device in the injector. As long as the injector is closed, wherein a fluid connection to a combustion chamber assigned to the injector is blocked, the quantity limiting valve is arranged in its first functional position. When the injector is opened, fuel flows out of the discharge area into the combustion chamber. Therefore, the pressure falls in the discharge area, and there is a pressure difference across the piston between the inflow region and the
- Fuel can flow over this from the inflow region in the outflow region, as the combustion chamber is supplied via the injector from the outflow area.
- the pressure difference between the inflow region and the outflow region thus remains, and the piston continues to shift in the direction of the outflow region as long as the injector is open. If this is closed, fuel continues to flow out of the inflow region via the fluid connection into the outflow region due to the pressure difference which initially persists, the pressure difference being increasingly compensated.
- Outflow region of the injector from which fuel flows into the combustion chamber, is fluidically separated. It can then no longer get fuel from the inflow into the outflow. This therefore runs in the combustion chamber empty, which at the same time maximizes the pressure difference across the piston to the inflow region.
- the piston is therefore permanently urged by the pressure prevailing in the inflow region pressure against the sealing surface, so that no fuel can get into the combustion chamber.
- the internal combustion engine is effectively protected from being damaged by an excessive amount of fuel.
- a disadvantage of a known quantity limiting valve is that the piston is delayed at the beginning of an injection with respect to the start of injection and abruptly released from its seat in the first functional position.
- the abrupt release of the piston leads to a superposition of the pressure profile
- Quantity control valve Accordingly, erroneous evaluations of the pressure signal detected in the single memory are unavoidable.
- the invention has for its object to provide a flow control valve, which does not have the disadvantages mentioned.
- the flow control valve With the flow control valve a delayed and sudden release of the piston from its seat in the first functional position and thus the formation of a ⁇ ffhungswelle be avoided.
- this should make it possible to evaluate a pressure signal in a single memory, which is assigned to an injector, error-free and reproducible, wherein in particular a
- Injection start can be reliably detected.
- Claim 1 is created. This is characterized by the fact that in one
- an underflow structure is formed, which comprises at least one intermediate space between the piston and the stopper member, which is in fluid communication with the inflow region.
- the at least one intermediate space is preferably in fluid connection with the fluid connection, in particular with the flow path arranged between the circumferential surface of the piston and the inner surface of the cylinder, so that a small amount of fuel can already flow from the inflow region into the outflow region directly when the injector is opened additional fluid path is opened from the inflow region to the outflow region via the piston.
- A preferably in a single memory of the
- a quantity limiting valve is preferred, which is characterized in that the underflow structure at least one extending to the stop surface
- Projection comprises, which has the end face at least partially. Instead of a flat end face, therefore, at least one projection facing the stop element-as seen in the axial direction-is provided on the piston, the end face being arranged at least in regions on an axial end of the projection facing the stop element.
- the underflow structure comprises more than one projection, wherein on each projection a portion of the end surface is arranged. In its first functional position, the piston with the at least one projection is biased against the abutment surface, wherein the at least one projection adjacent, in particular - seen in the circumferential direction - between the projections, the at least one gap is formed in the fuel in the first functional position comes out of the inflow area.
- the underflow structure comprises at least one recess extending into the end face.
- the underflow structure has more than one recess.
- the at least one gap is formed by the recess, wherein in the first
- a quantity limiting valve is also preferred, which is characterized in that the underflow structure comprises at least one projection which extends to the end face and which has the stop face at least in regions.
- the underflow structure is at least not exclusively on the piston, but also or possibly completely provided on the stop element, namely in the form of at least one projection on which the stop surface is arranged at least partially.
- more than one protrusion is provided on the abutment member, each protrusion having a portion of the abutment surface.
- the at least one intermediate space is adjacent to the at least one projection and particularly preferably-seen in the circumferential direction-between the projections.
- the underflow structure preferably comprises at least one recess extending into the abutment surface.
- the at least one intermediate space is formed in this case by the at least one recess.
- the underflow structure comprises at least one projection and / or at least one recess in the region of the piston, as well as at least one projection and / or at least one recess in the region of the stop element. The embodiments described above can therefore be combined with each other.
- the stop element is designed as a stop sleeve, which engages partially in the cylinder.
- the stop sleeve with a collar which runs along an outer circumference of the same, on a wall of the cylinder - seen in the axial direction - on.
- the stop element is therefore preferably designed as a separate, separate from the cylinder component, which is advantageous in terms of easy processing of the stop surface.
- the stop sleeve preferably protrudes into the cylinder, so that the contact area of the end face is arranged with the abutment surface in an interior of the cylinder. This ensures that the piston is guided safely in the cylinder at all times.
- a mass limiting valve is also preferred, which is characterized in that the piston has at least one projection extending in the direction of the stop surface, on which the end face is arranged. Preferably, the piston has three such projections. Alternatively or additionally, the piston preferably has at least one
- Recess preferably three recesses provided in the end face or is introduced into the end face / are.
- the choice of three projections and / or three recesses results in a particularly position-stable contact between the piston on the one hand and the stop element on the other.
- the stop sleeve at least one extending in the direction of the end face of the piston projection having the abutment surface, preferably three such projections, which together have the abutment surface, and / or at least one recess, preferably three recesses in the
- the three projections are symmetrical about a longitudinal axis of the
- the three recesses are preferably arranged symmetrically about the longitudinal axis of the flow control valve, wherein they particularly preferably have an angular distance of 120 ° to each other. Also in an embodiment in which the piston and / or the stop element is less than three or more than three
- Projections and / or recesses include / include these are preferably symmetrical, in particular at equal angular intervals, arranged around the longitudinal axis of the quantity limiting valve.
- the corresponding longitudinal direction also corresponds to the flow direction of the fuel from the inflow region into the outflow region.
- a circumferential direction is a direction concentrically surrounding the longitudinal direction.
- a radial direction is a direction perpendicular to the longitudinal direction.
- a flow control valve which is characterized in that at least one recess is formed as extending in the radial direction groove.
- Such a groove is particularly easy to manufacture and has aerodynamic advantages.
- a flow control valve which is characterized in that the stop sleeve has a - extending in the longitudinal direction - through hole, which forms at least partially the inflow region.
- the through-bore is therefore preferably at least part of a fuel reservoir or serves to pass fuel to the injector.
- it is preferably part of the high pressure line extending from the high pressure source to the injector.
- a flow control valve is preferred, which is characterized in that the at least one groove with the inflow region on the one hand and with the flow path between the peripheral surface of the piston and the inner surface of the cylinder on the other hand in
- the at least one groove forms not only a gap of the underflow structure, but at the same time a fluid path, via which fuel from the inflow region via the groove and the flow path in immediately upon opening of the injector can flow the outflow area.
- the at least one groove contributes significantly to the fact that the piston is neither late nor abruptly from its seat in the first
- a gap arranged between two projections can also be regarded as a groove in the sense explained here, wherein the intermediate space preferably extends in the radial direction.
- the gap is preferably with the
- the quantity limiting valve is preferably in an injection system for a
- Used quantity limiting valve in conjunction with an injector which has a single memory as an additional buffer volume.
- the quantity limiting valve is preferably integrated in the injector and particularly preferably downstream of the
- the quantity limiting valve can be used for any fuels that by means of an injector into a combustion chamber of a
- Fluid fuels of the type relevant here include both liquid and gaseous fuels.
- the flow control valve is suitable for injecting gasoline, diesel,
- Hydrogen or synthesis gas namely a mixture of hydrogen and carbon monoxide, can also be injected by means of the quantity limiting valve.
- the quantity limiting valve is particularly preferably used in conjunction with liquid fuels under normal conditions.
- An internal combustion engine, in which the quantity limiting valve is used is preferably designed as a reciprocating piston engine and can serve the propulsion of land, water or air vehicles.
- these are heavy agricultural machinery, mining vehicles or large construction machinery. It is also possible that through the
- Internal combustion engine defense serving vehicles such as tanks
- a corresponding internal combustion engine to drive a ship.
- Stationary applications in particular for energy generation, for example in a block heating power value, are possible.
- the internal combustion engine can be used in particular as an emergency generator, for continuous load operation or peak load operation.
- the internal combustion engine can drive stationary ancillary or auxiliary units, for example
- Figure 1 is a schematic representation of a first embodiment of a
- Figure 2A is a schematic bottom view of a stop element of the first
- Figure 2B is a schematic side view of the stop element according to Figure 2A.
- Figure 3 is a three-dimensional, schematic exploded view of parts of a
- Fig. 1 shows a schematic representation of an embodiment of a
- volume limiting valve 1 in longitudinal section is integrated here in an injector 3, wherein the injector 3 has a single memory 5.
- the injector 3 is part of an injection system 6 of an internal combustion engine 8, wherein the injection system 6 has a common high-pressure accumulator.
- the single memory 5 serves as additional
- the quantity limiting valve 1 has an inflow region 7 and an outflow region 9.
- a cylinder 11 is a piston 13 - in the axial direction or in
- the overflow channel 15 opens on the one hand into the inflow region 7 and on the other hand into a
- Flow path 17 which is disposed between a peripheral surface 19 of the piston 13 and an inner surface 21 of the cylinder 11.
- Lengthwise extending webs are provided on the peripheral surface 19, wherein in each case - seen in the circumferential direction - between the webs of the flow path 17 remains free. If, on the other hand, the projections 23 are axially offset relative to one another and overlapping in the circumferential direction, a tortuous flow path 17 results, along which the fuel flowing past flows around the projections 23 in turns.
- the piston 13 is shown in its first functional position in which it bears with an end face 25 on a stop surface 27 of a stop element 29 under prestress.
- the piston 13 is urged in the illustrated embodiment by a spring 31 under bias against the stop element 29.
- the piston 13 remains in its first functional position as long as the injector 3 is closed. When the injector 3 is opened, fuel flows out of the outflow region 9 through a
- Inflow region 7 and the outflow region 9 acts on the piston 13, a force which eventually exceeds the spring force 31 caused by the biasing force.
- the piston 13 is then displaced in the longitudinal direction towards the outflow region 9 or into it - downwards in FIG. 1. As soon as no contact between the piston 13 and the
- Stop element 29 is given, in addition, fuel can flow directly into the flow path 17, so that two fluid paths between the inflow region 7 and the
- Outflow area 9 namely a fluid path in which the overflow channel 15 is provided upstream of the flow path 17, and another, in which the fuel flows directly from the inflow region 7 in the flow path 17.
- the flow cross sections of these flow paths are dimensioned such that more and more fuel flows out of the outflow region 9 via the outflow region 33 than can flow in from the inflow region 7 via the fluid paths.
- the pressure difference between the inflow region 7 and the outflow region 9 is thus retained, and the piston 13 continues to move into the outflow region 9, as seen in the longitudinal direction, as long as the injection continues.
- Pressure difference is a limit from which the force exerted by the spring 31 on the piston 13 biasing force is greater than the force caused by the pressure difference, opposing force, so that the piston 13 reverses and moves back towards the stop member 29. Finally, it reaches - preferably before the next injection event - again its first functional position.
- the injector 3 If the injector 3 is defective, so that fuel permanently escapes from it, the pressure difference remains above the piston 13, so that it displaces as far as a sealing surface 35 at which it exits finally sealingly abuts with an axial end surface 37.
- the piston 13 is then arranged in a second functional position.
- the inflow region 7 is fluidically separated from the outflow region 9 downstream of the piston 13 or from the outflow region 33 upstream of the piston 13, so that no more fuel can flow from the inflow region 7 into the outflow region 9 or into the outflow region 33.
- the outflow region 9 and the outflow region 33 run empty, wherein the
- volume limiting valve at an opening of the injector thus at the start of injection, delayed and suddenly released from its first functional position. This creates a so-called ⁇ ffhungswelle, namely a temporally local pressure increase in a in the region of
- the underflow structure 39 is arranged completely on the stop element 29, wherein in particular projections 43 are provided which extend in the direction of the end face 25 and on which the stop face 27 is arranged in some areas. Between the projections 43, of which only one is shown in FIG. 1, the intermediate spaces 41 are formed, of which only one is shown in FIG. Alternatively, it is possible that in the stop surface 27 recesses, in particular grooves are introduced, which act as gaps 41.
- FIG. 2A shows a schematic view of the stop element 29 according to FIG. 1 from below.
- the projections 43 can be seen, wherein the stop element 29, which is designed here as a stop sleeve 48, three projections 43 which - seen in the circumferential direction - are arranged symmetrically and in particular at an angular distance of 120 ° to each other. Between the projections 43 - seen in the circumferential direction - the gaps 41 are arranged. It is also possible in the illustrated embodiment, the interstices 41 to interpret as recesses 44, which are provided in the abutment surface 27. It also appears that the abutment surface 27 is arranged on the projections 43 and is interrupted by the recesses 44 or the intermediate spaces 41.
- the stop element 29 has a through hole 45 extending in the longitudinal direction, which is also shown in FIG.
- the through-bore 45 forms the inflow region 7 in regions.
- FIG. 2B shows a schematic side view of the exemplary embodiment of a stop element 29 according to FIG. 2A.
- the stop element 29 preferably has a collar 49 which runs around along an outer circumference 47 and which is also shown in FIG. It is shown in Figure 1 that the stop sleeve 48 and the stop member 29 rests with the collar 49 on a wall 51 of the cylinder 11.
- the effective flow cross section of the fluid connection between the inflow region 7 and the outflow region 9 via the piston 13 is smaller than the flow cross section
- the projections 43 have a small height h. This is preferably from at least a few tenths mm to a maximum of 2 mm, more preferably a few tenths mm, more preferably five tenths mm.
- FIG. 3 shows a schematic, three-dimensional view of a second exemplary embodiment of a quantity limiting valve 1. Identical and functionally identical elements are provided with the same reference symbols, so that reference is made to the preceding description.
- the illustration according to FIG. 3 corresponds to a schematic exploded view, wherein only selected parts of the quantity limiting valve 1 are shown.
- the stop element 29 designed as a stop sleeve 48 is shown with the collar 49.
- this has the projections 23, of which at least one side of the recess 53 facing the viewer is shown here.
- FIG. 3 Also shown in FIG. 3 is the overflow channel 15, which on the one hand opens into a central region 55 of the piston 13, wherein the central region 55 is also shown in FIG. 1, and on the other hand opens into the region of a recess 53, here in FIG the
- Viewer is arranged facing away.
- three recesses 56 are introduced in the form of grooves 57 in the end face 25 of the piston 13, which are formed as radial grooves. Is the piston 13 with the end face 25 on the abutment surface 27 in its first Functional position under bias, the grooves 57 form spaces 41, which are underflowed by fuel, wherein the grooves 57 a fluid connection between the
- Recesses 56 are provided, as well as in the area of the stop surface 27th
- Quantity limiting valve 1 is preferably used in conjunction with injectors 3, which are provided for the direct injection of fuel into combustion chambers of the internal combustion engine 8. However, it is also possible, the quantity limiting valve 1 in
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013210983.0A DE102013210983B4 (en) | 2013-06-12 | 2013-06-12 | Flow control valve |
PCT/EP2014/001490 WO2014198387A1 (en) | 2013-06-12 | 2014-06-03 | Quantity-limiting valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3008327A1 true EP3008327A1 (en) | 2016-04-20 |
EP3008327B1 EP3008327B1 (en) | 2018-05-23 |
Family
ID=50942254
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14729857.4A Active EP3008327B1 (en) | 2013-06-12 | 2014-06-03 | Quantity-limiting valve |
Country Status (7)
Country | Link |
---|---|
US (1) | US9909547B2 (en) |
EP (1) | EP3008327B1 (en) |
JP (1) | JP2016520767A (en) |
CN (1) | CN105264216B (en) |
DE (1) | DE102013210983B4 (en) |
HK (1) | HK1220243A1 (en) |
WO (1) | WO2014198387A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016101425B4 (en) * | 2016-01-27 | 2018-05-09 | Firma L'orange Gmbh | Quantity limiting valve, in particular for a high-pressure pump system |
DE102017202310A1 (en) * | 2017-02-14 | 2018-08-16 | Robert Bosch Gmbh | Throttle element and low-pressure circuit of a fuel injection system with a throttle element |
DE102019121156A1 (en) * | 2019-08-06 | 2021-02-11 | Woodward L'orange Gmbh | Use for a flow control valve |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3341575C2 (en) * | 1983-11-17 | 1996-06-05 | Bosch Gmbh Robert | Pressure valve for fuel injection pumps |
US5295469A (en) * | 1990-07-09 | 1994-03-22 | Nippondenso Co., Ltd. | Safety valve for fuel injection apparatus |
US5678521A (en) * | 1993-05-06 | 1997-10-21 | Cummins Engine Company, Inc. | System and methods for electronic control of an accumulator fuel system |
DE4414242A1 (en) * | 1994-04-23 | 1995-10-26 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
US6082332A (en) * | 1994-07-29 | 2000-07-04 | Caterpillar Inc. | Hydraulically-actuated fuel injector with direct control needle valve |
DE19640085C2 (en) * | 1996-09-28 | 2001-10-25 | Orange Gmbh | Stop valve to limit the flow rate |
JP3521811B2 (en) * | 1999-08-05 | 2004-04-26 | 株式会社デンソー | Safety devices for internal combustion engines |
JP4140175B2 (en) * | 2000-07-21 | 2008-08-27 | 株式会社デンソー | Accumulated fuel injection device for internal combustion engine |
JP3873235B2 (en) * | 2002-06-26 | 2007-01-24 | ボッシュ株式会社 | Flow limiter |
FI117643B (en) * | 2003-01-15 | 2006-12-29 | Waertsilae Finland Oy | Arrangements at fuel injection plant |
JP4100393B2 (en) * | 2004-10-29 | 2008-06-11 | 株式会社デンソー | Flow damper |
DE102007055750B4 (en) * | 2006-12-27 | 2021-02-11 | Denso Corporation | Flow damper |
EP2423498B1 (en) * | 2010-08-26 | 2013-09-11 | Wärtsilä Schweiz AG | Passive flow control valve |
AT510464B1 (en) * | 2010-09-27 | 2012-07-15 | Bosch Gmbh Robert | VALVE WITH PRESSURE LIMITING FUNCTION |
US20140373806A1 (en) * | 2012-01-05 | 2014-12-25 | Deyang Hou | Fuel injector for multi-fuel injection with pressure intensification and a variable orifice |
AT513158B1 (en) * | 2012-04-10 | 2014-03-15 | Bosch Gmbh Robert | Flow restrictor with ball and throttle |
-
2013
- 2013-06-12 DE DE102013210983.0A patent/DE102013210983B4/en not_active Expired - Fee Related
-
2014
- 2014-06-03 EP EP14729857.4A patent/EP3008327B1/en active Active
- 2014-06-03 CN CN201480033589.3A patent/CN105264216B/en not_active Expired - Fee Related
- 2014-06-03 JP JP2016518860A patent/JP2016520767A/en active Pending
- 2014-06-03 WO PCT/EP2014/001490 patent/WO2014198387A1/en active Application Filing
-
2015
- 2015-12-07 US US14/960,870 patent/US9909547B2/en not_active Expired - Fee Related
-
2016
- 2016-07-13 HK HK16108202.9A patent/HK1220243A1/en not_active IP Right Cessation
Non-Patent Citations (1)
Title |
---|
See references of WO2014198387A1 * |
Also Published As
Publication number | Publication date |
---|---|
US20160084210A1 (en) | 2016-03-24 |
HK1220243A1 (en) | 2017-04-28 |
DE102013210983B4 (en) | 2021-04-29 |
US9909547B2 (en) | 2018-03-06 |
JP2016520767A (en) | 2016-07-14 |
CN105264216B (en) | 2017-11-17 |
WO2014198387A1 (en) | 2014-12-18 |
EP3008327B1 (en) | 2018-05-23 |
CN105264216A (en) | 2016-01-20 |
DE102013210983A1 (en) | 2014-12-18 |
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Legal Events
Date | Code | Title | Description |
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