EP3040550B1 - Kraftstoffinjektor - Google Patents

Kraftstoffinjektor Download PDF

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Publication number
EP3040550B1
EP3040550B1 EP15003476.7A EP15003476A EP3040550B1 EP 3040550 B1 EP3040550 B1 EP 3040550B1 EP 15003476 A EP15003476 A EP 15003476A EP 3040550 B1 EP3040550 B1 EP 3040550B1
Authority
EP
European Patent Office
Prior art keywords
fuel
volume
fuel injector
volumes
storage volume
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.)
Not-in-force
Application number
EP15003476.7A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3040550A1 (de
Inventor
Dino Imhof
Georg Tinschmann
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.)
Innio Jenbacher GmbH and Co OG
Original Assignee
GE Jenbacher GmbH and Co OHG
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 GE Jenbacher GmbH and Co OHG filed Critical GE Jenbacher GmbH and Co OHG
Publication of EP3040550A1 publication Critical patent/EP3040550A1/de
Application granted granted Critical
Publication of EP3040550B1 publication Critical patent/EP3040550B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0663—Details on the fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02D19/0686—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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • 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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • 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
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
    • 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
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator

Definitions

  • the invention relates to a fuel injector having the features of the preamble of claim 1, an internal combustion engine having such a fuel injector and a method for operating an internal combustion engine.
  • Fuel injectors of modern internal combustion engines operate with high fuel pressures.
  • a storage volume is provided in the injector itself, from which the fuel is removed for injection and in which fuel from the fuel supply line via a throttle (orifice) can flow.
  • a vibration isolation of the injector from the fuel supply is for example from the DE 10 2006 051 583 A1 known.
  • said storage volume must be in a specific ratio to the quantity of fuel taken from the fuel injector into the combustion chamber, which is taken in a switching operation. If the storage volume is too small, the pressure in the storage volume during injection breaks down too much; larger volumes are harder to realize due to space limitations.
  • the damping effect is determined from the interaction of storage volume and throttle, the flow cross-section, d. H. the hydraulic damping effect of the throttle adapted to the size of the storage volume.
  • a fuel injector should have a high turndown ratio .
  • the turndown ratio A fuel injector is the ratio of the maximum and minimum amounts of fuel that a fuel injector can inject in a controlled manner. If a fuel injector can represent a fuel quantity of 0.5% to 100%, this fuel injector has a turndown ratio of 200. This is particularly relevant for dual-fuel engines operating in 100% diesel operating modes to low diesel pilot injection gas operation. Of particular importance is that the turndown ratio should be in a controlled and reproducible manner over the lifetime of the fuel injector.
  • the object of the invention is therefore to provide a fuel injector which can be used over wide areas of the injection quantity, without having the disadvantages of the prior art. Also, an internal combustion engine and a method for operating the same are to be specified.
  • the size of the storage volume can thus be adapted to the respective injection quantity.
  • the injection quantities may differ depending on the operating state of the internal combustion engine.
  • the changeability in the enterprise brings substantial advantages with itself.
  • a double version of fuel injectors in which separate fuel injectors are provided for different operating conditions.
  • Operating conditions are, for example, the diesel operation, in which all the fuel is supplied as diesel and the dual-fuel operation, in which diesel is supplied only for ignition (so-called pilot injection) and in small quantities.
  • the variability of the storage volume during operation means that the internal combustion engine does not have to be switched off to change the storage volume.
  • the storage volume corresponds to about 30 to 80 times the amount injected.
  • the storage volume consists of at least two partial volumes, which are connected via a switching element so that they act as a total volume, preferably within the injector. It may be provided that the total volume is matched to the larger injection quantity.
  • the storage volume is not formed by a single cavity, but by at least two partial volumes, which are interconnected.
  • the at least second partial volume can be brought into fluid communication with the first partial volume, whereby a larger volume of the storage volume is available for the withdrawal of fuel during the injection.
  • the arrangement of the at least two sub-volumes is fluidically parallel.
  • both or all of the at least two partial volumes depend on the high-pressure fuel line.
  • the switching element is then arranged downstream of the one partial volume and can be actuated in such a way that it blocks off this partial volume.
  • only the second subvolume is in communication with the nozzle assembly. During the injection process so fuel is removed only from this additional sub-volume.
  • the arrangement can also comprise more than two partial volumes. These can then be closed or opened by further switching elements. In practice, this will hardly be realized for reasons of space alone.
  • the arrangement of the at least two sub-volumes is fluidically serial.
  • the switching element is then arranged, for example, fluidically between the sub-volumes.
  • the switching element is designed so that a subsequent flow of fuel is ensured in the downstream partial volume. This can be realized, for example, by an always remaining opening in the closed position, through which then fuel can flow in like a throttle.
  • the fuel may be, for example, gasoline, diesel or heavy fuel oil.
  • Protection is also desired for an internal combustion engine having a fuel injector according to the invention and a method for operating an internal combustion engine.
  • the injection characteristic can therefore be adapted to different operating states of the internal combustion engine.
  • FIG. 1 shows a fuel injector 1 with storage volume 20 according to the prior art.
  • a dotted frame visualizes the system limits of the fuel injector. 1
  • a high-pressure fuel line 8 supplies the fuel injector 1 with fuel via a diaphragm 3. Downstream of the diaphragm 3, a storage volume 20 integrated in the fuel injector 1 is arranged. The orifice 3 reduces pressure oscillations and mitigates deviations from cylinder to cylinder.
  • the fuel injector 1 shown has a pressure sensor 9 on the storage volume 20.
  • a line leads to a nozzle assembly 10.
  • the nozzle assembly 10 can be actuated by a control valve 6. Between control valve 6 and nozzle assembly 10 inlet and outlet throttles 2 are arranged.
  • the nozzle assembly has a hydraulically actuable needle through which fuel is released. The needle is controlled by the control valve 6 together with the inlet and outlet throttles 2.
  • a flow restrictor 14 is provided as a safety element in the supply line to the nozzle assembly 10, but not mandatory.
  • Fig. 2 shows the pressure curve in the storage volume 20 during an injection process, as is known from the prior art.
  • a pressure sensor 9 is arranged on the storage volume 20, with which the pressure changes during the injection process can be detected. Plotted in the diagram is the pressure in the storage volume 20 in bar above the crank angle in degrees. The timing of the events presented is expressed in degrees crank angle. The pressure in the storage volume 20 corresponds to the pressure in the high-pressure fuel line 8 ( high pressure rail ) before the beginning of the injection.
  • the fuel injector 1 At time SOC ( start of current ), the fuel injector 1 is energized, so that after a dead time T t, the injection begins.
  • the injection duration is denoted by reference ID.
  • the observed pressure drop in the storage volume 20 is indicated in the diagram by ⁇ p.
  • the injected fuel quantity or mass can be calculated from the pressure profile. In other words, the amount of fuel injected is a function of these quantities.
  • FIG. 3 shows a fuel injector 1 according to the invention according to a first embodiment.
  • Two partial volumes 21, 22 are arranged serially.
  • the partial volumes 21, 22 together result in the storage volume 20.
  • a first aperture 3 is provided between the first part volume 21 and the high pressure fuel line 8 .
  • a further diaphragm 7 is arranged between the storage volumes 21 and 22, a further diaphragm 7 is arranged.
  • the panel 7 is bypassed by a switching element 12 in the form of a bypass.
  • the switching element 12 in the form of an electrically actuated switching valve executed.
  • Other embodiments of the switching element 12 are conceivable, for example, pneumatically or hydraulically actuated valves.
  • the switching element 12 is closed.
  • the further diaphragm 7 is designed such that fluid from the partial volume 21 can flow into the partial volume 22 only with great delay. In other words, only a small free diaphragm cross-section between the partial volumes 21 and 22 is available, so that the extraction characteristic is largely determined by the partial volume 22.
  • the switching element 12 is switched so that it releases a larger free total flow cross-section.
  • the storage volumes 21 and 22 communicate largely unthrottled with each other, so that the extraction characteristic of the common volume 20, ie the sum of the sub-volumes 21, 22 corresponds.
  • the arrangement of the sub-volumes 21 and 22 is designed so that the sub-volume 22 has the space suitable for the dual-fuel mode volume. This means, as explained above, that the volume of the partial volume 22 corresponds to approximately 30 to 80 times the injection quantity in the dual-fuel mode.
  • the sub-volume 21, however, is dimensioned so that in connection with the sub-volume 22, a total volume 20 of the sub-volumes 21 and 22 sets, which corresponds to 30 to 80 times the amount of injection quantity of diesel operation.
  • the injection quantity of the diesel operation is 100% with a volume of 1000 mm 3 to be injected per working cycle. This results in an acceptable total volume in the range of 30,000 to 80,000 mm 3 (thirty thousand to eighty thousand) for the volume of the total volume of the partial volumes 21 and 22.
  • the size of the partial volume 22 for the dual-fuel operation is 1/200 (1/100) of the total volume of the partial volumes 21 and 22, ie in a range of 150 to 400 (100). 300 to 800) mm 3 .
  • the values in brackets refer to a turndown ratio of 100.
  • a pressure sensor 9 may be arranged at the storage volume 22 .
  • the arrangement according to the invention of the partial volumes means that the respective volume used and the injection quantity are in an adapted ratio, which makes a more accurate measurement of the pressure curve possible during the injection. This in turn allows a more accurate calculation of the injection quantity.
  • the prior art nozzle assembly 10 This consists in this example of a control valve 6 hydraulically actuated injection needle, which receives switching pulses via a control device 11.
  • the injection needle can also be realized as a piezo injector. In this case, of course, eliminates the necessary components for a hydraulic actuation of the nozzle assembly 10th
  • a flow restrictor 14 is provided as a safety element in the supply line to the nozzle assembly 10, but not mandatory.
  • FIG. 4 shows an embodiment with a parallel arrangement of the sub-volumes 21 and 22.
  • the sub-volumes 21 and 22 of the storage volume 20 are arranged fluidically parallel.
  • the partial volume 21 is fed via the diaphragm 3 from the high-pressure fuel line 8.
  • the storage volume 21 can be switched on and off via an electrically operable switching element 12.
  • the switching element 12 is closed.
  • the fluid connection between partial volume 21 and nozzle assembly 10 is interrupted.
  • the injection characteristic is determined by the partial volume 22, which is made smaller.
  • the partial volume 22 is fed via a further diaphragm 15 from the high-pressure fuel line 8.
  • both partial volumes 21, 22 are available for removal.
  • the switching element 12 is a switched directly from the pressure in the sub-volume 21 valve.
  • the fuel injector 1 need not be provided with two inputs for the high-pressure fuel line 8. It is also sufficient an input that branches in front of the partial volumes 21, 22 in a suitable manner.
  • This variant is in the FIG. 4 dashed lines with aperture 16 shown: in this case replaced the aperture 16, the aperture 15. The line section to the high-pressure fuel line 8, in which the aperture 15 is omitted. The connection with the high-pressure fuel line 8 then takes place via the diaphragm 3.
  • a pressure sensor 9 can be set up again.
  • the remaining structure of the fuel injector 1 corresponds to that of FIG. 3 , The advantages are the same as for the embodiment of FIG. 3 described. As a numerical example, the values for FIG. 3 be used.
  • FIG. 5 shows an embodiment with variable partial volumes 21, 22.
  • a displaceable piston 18 is provided, which divides the partial volumes 21, 22 from each other.
  • the content of the partial volume 21 communicates with the spring chamber 24th
  • the (smaller) sub-volume 22 is in fluid communication with the nozzle assembly 10, ie, the injection quantity is withdrawn from the sub-volume 22, as required in dual-fuel mode, for example.
  • the throttling with respect to the high-pressure fuel line takes place in this operating state via the diaphragm 4.
  • the spring chamber 24 in which the spring assembly 19 is depressurized Upon actuation of the control valve 23, the spring chamber 24 in which the spring assembly 19 is depressurized. Then, in this illustration, the piston 18 moves down.
  • the partial volume 21 is connected to the overflow line 17 to the supply to the partial volume 22: as soon as the piston 18 exceeds a predetermined position, the previously closed by the piston 18 overflow 17 is released.
  • the piston 18 thus acts as a slide relative to the overflow line 17.
  • the previously separate partial volumes 21, 22 are connected to each other. The removal then takes place from the sum volume formed by the partial volumes 21, 22.
  • This operating position is selected for the diesel operation, are accessed in the larger injection quantities.
  • FIG. 6 An alternative embodiment with variable partial volumes 21, 22 is shown in FIG FIG. 6 shown.
  • the piston 18 closes the partial volume 21 with respect to the partial volume 22 as long as the control valve 23 remains closed. The removal takes place in this state from the (smaller) sub-volume 22, as required for example in dual-fuel mode.
  • the plate (not shown in the figure) of the piston 18 thereby releases the partial volume 22 with respect to the partial volume 21.
  • the previously separate partial volumes 21, 22 are connected to each other.
  • the removal then takes place from the total volume formed by the partial volumes 21, 22, as is advantageous, for example, in diesel operation.
  • the connection of the partial volumes 21, 22 is produced.
  • FIG. 7 shows the pressure curve in the storage volume, shown over the crank angle in degrees in the case of taking the small amount of fuel during the injection process in dual-fuel operation.
  • the solid (top) line shows this pressure curve at the storage volume 20, which in another scale also in FIG. 2 is shown.
  • the dashed line shows the pressure curve for a fuel injector 1 according to the invention on the partial volume 22. This results in a clear, easily measurable pressure curve.
  • the rail pressure (pressure in the high-pressure fuel line 8) is typically in the range from 1000 bar to 2500 bar.
  • the observed in the injection process pressure drop according to the prior art is in the order of a few bar in dual-fuel operation and of about 100 bar in diesel mode.
  • the pressure drop observed in the injection process according to the invention is of the order of e.g. 50 to 100 bar in dual-fuel operation or of approx. 100 bar in diesel operation.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Fuel-Injection Apparatus (AREA)
EP15003476.7A 2015-01-02 2015-12-07 Kraftstoffinjektor Not-in-force EP3040550B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ATA5/2015A AT515933B1 (de) 2015-01-02 2015-01-02 Kraftstoffinjektor

Publications (2)

Publication Number Publication Date
EP3040550A1 EP3040550A1 (de) 2016-07-06
EP3040550B1 true EP3040550B1 (de) 2018-09-05

Family

ID=54834605

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15003476.7A Not-in-force EP3040550B1 (de) 2015-01-02 2015-12-07 Kraftstoffinjektor

Country Status (7)

Country Link
US (1) US10006396B2 (ko)
EP (1) EP3040550B1 (ko)
JP (1) JP6144750B2 (ko)
KR (1) KR101797324B1 (ko)
CN (1) CN105822474B (ko)
AT (1) AT515933B1 (ko)
BR (1) BR102015032599A2 (ko)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6614195B2 (ja) * 2017-04-06 2019-12-04 トヨタ自動車株式会社 内燃機関の制御装置
CN111058985B (zh) * 2020-01-16 2024-05-17 无锡威孚高科技集团股份有限公司 用于双燃料喷射器的测量装置
CN112191379B (zh) * 2020-09-22 2022-03-29 柳州延龙汽车有限公司 一种多功能的高压清洁机喷头
DE102021200154A1 (de) * 2021-01-11 2022-07-14 Robert Bosch Gesellschaft mit beschränkter Haftung Kraftstoffeinspritzvorrichtung

Family Cites Families (18)

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Publication number Priority date Publication date Assignee Title
US6336598B1 (en) * 1998-09-16 2002-01-08 Westport Research Inc. Gaseous and liquid fuel injector with a two way hydraulic fluid control valve
US6761325B2 (en) * 1998-09-16 2004-07-13 Westport Research Inc. Dual fuel injection valve and method of operating a dual fuel injection valve
DE10123911A1 (de) * 2001-05-17 2002-11-28 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung mit Druckübersetzungseinrichtung und Druckübersetzungseinrichtung
DE10210282A1 (de) * 2002-03-08 2003-09-25 Bosch Gmbh Robert Vorrichtung zum Einspritzen von Kraftstoff an stationären Verbrennungskraftmaschinen
JP2004036423A (ja) * 2002-07-01 2004-02-05 Mitsubishi Heavy Ind Ltd 燃料噴射装置およびこれを備えたディーゼル機関
DK1793121T3 (da) 2002-07-01 2009-04-14 Mitsubishi Heavy Ind Ltd Brændstofinjektor og dieselmotor omfattende samme
DE10344181A1 (de) 2003-09-24 2005-04-28 Mtu Friedrichshafen Gmbh Verfahren zur Steuerung und Regelung einer Brennkraftmaschine
JP4391344B2 (ja) * 2004-07-02 2009-12-24 本田技研工業株式会社 内燃機関の燃料圧制御装置
FR2872865B1 (fr) * 2004-07-07 2009-01-16 Renault Sas Dispositif d'injection a rampe commune avec amortissement des ondes de pression
WO2007009279A1 (de) * 2005-07-18 2007-01-25 Ganser-Hydromag Ag Speichereinspritzsystem für brennkraftmaschine
JP2007132215A (ja) * 2005-11-08 2007-05-31 Toyota Motor Corp 燃料噴射装置
DE102006051583A1 (de) * 2006-11-02 2008-05-08 Robert Bosch Gmbh Kraftstoffinjektor mit Speichervolumensegment
JP2010164037A (ja) * 2009-01-19 2010-07-29 Toyota Motor Corp 燃料噴射装置
JP2010180797A (ja) * 2009-02-06 2010-08-19 Toyota Motor Corp 燃料噴射弁
AT509877B1 (de) 2010-11-02 2011-12-15 Bosch Gmbh Robert Vorrichtung zum einspritzen von kraftstoff in den brennraum einer brennkraftmaschine
US9376992B2 (en) * 2012-06-04 2016-06-28 Caterpillar Inc. Dual fuel injector and fuel system
DE102013204289A1 (de) * 2013-03-12 2014-10-02 Robert Bosch Gmbh Kraftstoffeinspritzsystem für eine Brennkraftmaschine
DE102013021810B4 (de) * 2013-12-20 2017-02-23 L'orange Gmbh Dual-Fuel-Kraftstoffinjektor

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Publication number Publication date
CN105822474B (zh) 2018-12-28
CN105822474A (zh) 2016-08-03
AT515933A4 (de) 2016-01-15
EP3040550A1 (de) 2016-07-06
JP2016136017A (ja) 2016-07-28
KR101797324B1 (ko) 2017-12-12
JP6144750B2 (ja) 2017-06-07
US20160195033A1 (en) 2016-07-07
AT515933B1 (de) 2016-01-15
BR102015032599A2 (pt) 2016-10-04
US10006396B2 (en) 2018-06-26
KR20160083804A (ko) 2016-07-12

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