WO2017025241A1 - Kraftstoffhochdruckpumpe - Google Patents
Kraftstoffhochdruckpumpe Download PDFInfo
- Publication number
- WO2017025241A1 WO2017025241A1 PCT/EP2016/065163 EP2016065163W WO2017025241A1 WO 2017025241 A1 WO2017025241 A1 WO 2017025241A1 EP 2016065163 W EP2016065163 W EP 2016065163W WO 2017025241 A1 WO2017025241 A1 WO 2017025241A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- bore
- inlet
- fuel pump
- longitudinal axis
- Prior art date
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
- 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
- F02M59/462—Delivery 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
- 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
- F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
- F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid 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
- 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
- F02M63/005—Pressure relief 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
- 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
- F02M63/023—Means for varying pressure in common rails
- F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
- F02M63/0245—Means for varying pressure in common rails by bleeding fuel pressure between the high pressure pump and the common rail
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/0406—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded in the form of balls
Definitions
- the invention relates to a high-pressure fuel pump for a fuel injection system of an internal combustion engine.
- High-pressure fuel pumps in fuel injection systems are used to apply a high-pressure fuel, for example, in the case of gasoline internal combustion engines in the range of 250 bar - 400 bar and in diesel engines in the range of 2000 bar - 2500 bar.
- a high-pressure fuel for example, in the case of gasoline internal combustion engines in the range of 250 bar - 400 bar and in diesel engines in the range of 2000 bar - 2500 bar.
- the high-pressure fuel pump is typically designed as a piston pump, wherein a piston in a pressure chamber moves translationally and thus supplied to the pressure chamber
- the pressurized fuel is then usually via a high-pressure connection to a high pressure pressure range, z. B. a pressure chamber hydraulically downstream pressure accumulator, the so-called.
- Common rail supplied from where the fuel can then be injected via injectors into the combustion chambers of the combustion chambers.
- a pressure relief valve is provided which abgrest over ⁇ schüssigen fuel from the high pressure region of the fuel injection system to relieve this.
- DE 10 2004 013 307 A1 discloses a pressure-limiting valve in a high-pressure fuel pump, which is arranged in a blind bore and is in fluid communication with the pressure chamber via a bore arranged at an angle of approximately 90 ° relative to the blind bore.
- blind hole bore serves as dead water area and dirt reservoir until the pressure relief valve is activated, which should preferably be the case rarely. Only when the pressure relief valve is put into operation will accumulated dirt be transported into the pressure chamber.
- the object of the invention is to propose an improved in this respect high-pressure fuel pump.
- a high-pressure fuel pump has a pressure chamber arranged in a housing, which is bounded on one side by a piston surface on a piston which moves translationally in the pressure chamber along a movement axis.
- the pressure chamber is on the input side with a low pressure inlet to Supplying fuel to the pressure chamber and the output connected to a high-pressure port, which defines an outlet volume together with the housing.
- an inlet valve is arranged such that an inlet bore of the low-pressure inlet is separated from a directly hydraulically connected to the pressure chamber inlet volume of the low-pressure inlet.
- There is provided a pressure limiting valve for venting an overpressure in the outlet volume disposed in a bore extending from the outlet volume into the housing. The bore opens into the inlet volume of the low pressure inlet.
- the bore in which the pressure limiting valve is arranged is therefore no longer designed as a blind bore as hitherto known, but has a connection with the low-pressure inlet and that in the region in which the inlet valve is located. This prevents the previously existing blind bore from storing dirt until the pressure relief valve is activated and then transporting it to the high-pressure fuel pump, since the bore in which the
- Pressure relief valve is arranged, is rinsed consistently during operation of the high-pressure fuel pump.
- the bore is formed as a through hole having a receiving area for receiving the pressure relief valve and a connecting portion for establishing a hydraulic connection to the inlet volume.
- the connection area has a smaller cross section than the reception area.
- the pressure relief valve on a rear ⁇ spring having a longitudinal axis in the direction of force of the return spring, wherein the connecting portion is arranged coaxially with the longitudinal axis of the return spring.
- the receiving area of the bore has a
- the bore has a connection opening to the pressure chamber for the hydraulic connection of the bore to the pressure chamber.
- the connection area and the connection opening are separated from one another, for example, by at least one partial area of the end wall.
- connection area By arranging both the connection area and the connection opening, circulation of the fuel during operation is enabled. As a result, an accumulation of particles in a rear region of the bore, in which the pressure relief valve is arranged, is avoided or reduced.
- romance area advantageously form complementary flow cross sections
- the drain hole, over which the overpressure fuel is shut down completely displaced on the through hole compared to the usual arrangements.
- connection opening is arranged in a side wall of the bore extending parallel to the longitudinal axis of the return spring.
- an arrangement is preferably formed at an angle of approximately 90 ° to the connection region, so that the fuel to be separated off can be deactivated in different spatial directions.
- a high pressure connection longitudinal axis of the high pressure port extends substantially perpendicular to the axis of movement of the piston.
- a bore longitudinal axis of the bore, in which the pressure limiting valve is arranged is arranged at an angle between 1 ° and 10 °, in particular between 2 ° and 8 °, preferably between 4 ° and 6 °, to the high-pressure longitudinal axis.
- an outlet valve Hydraulically between the pressure chamber and outlet volume, an outlet valve is normally arranged, whose longitudinal axis is usually also arranged perpendicular to the axis of movement of the piston.
- This exhaust valve is usually in a hole in the housing of the high-pressure fuel pump.
- the bore longitudinal axis of the bore in We ⁇ sentlichen an angle between 95 ° and 105 °, in particular 98 ° and 102 °, to the axis of movement of the piston.
- Figure 1 is a longitudinal sectional view of a high-pressure fuel pump with a arranged in a bore pressure relief valve.
- Fig. 2 is a cross-sectional view through the line II-II in Fig.
- FIG. 3 is a longitudinal sectional view of the high-pressure fuel pump from FIG. 1 in a detail view in the region of the pressure-limiting valve;
- Fig. 4 is a longitudinal sectional view of the high-pressure fuel pump of Fig. 1 in a further detailed view in the region of a pressure chamber of the high-pressure fuel pump.
- a pressure chamber 14 is arranged, in which a piston 16 along a movement axis 18 moves up and down and so arranged in the pressure chamber 14 fuel periodically compacted and relaxed.
- the piston 16 which moves in the pressure chamber 14 has a piston surface 20 which delimits the pressure chamber 14 at the bottom.
- the pressure chamber 14 is connected on the input side to a low-pressure inlet 22.
- Pressurized fuel is fed on the output side via a high pressure port 24 to a high pressure region 25.
- the high pressure port 24 then carries the pressurized fuel further to, for example, a downstream common rail.
- an inlet valve 26 is arranged, which separates an inlet bore 28 from an inlet volume 30, which communicates directly with the pressure chamber 14 hydraulically.
- the inlet volume 20 is not part of the pressure chamber 14.
- the high pressure port 24 is configured to define, together with the housing 12, an exhaust volume 32 into which the pressurized fuel passes via an exhaust valve 34. From this outlet volume 32, a bore 36 extends into the housing 12. In the bore 36, a pressure relief valve 38 is arranged, the fuel from the high ⁇ pressure port 24 ab interviewedt when in the high pressure region 25 builds up too much pressure.
- Fig. 2 shows a cross-sectional view of the high-pressure fuel pump 10 along the line II-II in Fig. 1 in a view from above.
- the bore 36 in which the pressure limiting valve 38 is arranged, extends completely from the high-pressure port 24 or the outlet volume 32 up to the inlet volume 30.
- the bore 36 is therefore formed as a through hole 42.
- the bore 36 has a receiving region 44, in which the pressure limiting valve 38 is received, and further comprises a connecting portion 46, which establishes the connection between the receiving region 44 and the inlet volume 30 of the low-pressure inlet 22.
- the connection region 46 has a smaller cross-section than the receiving region 44, so that a restoring spring 48 of the pressure-limiting valve 38 can be supported on a resulting end wall 50 of the bore 36.
- the connecting portion 46 is thus disposed in the end wall 50.
- the return spring 48 has a longitudinal axis 52 which extends along a direction of force of the return spring 48.
- the bore 36 extends coaxially with this longitudinal axis 52 in such a way that also the connecting portion 46 coaxial with the
- a high-pressure connection is ⁇ longitudinal axis 54 of the high pressure port 24 perpendicular ⁇ right to the axis of movement 18 of the piston 16.
- a longitudinal axis 56 of the outlet valve 34 is also arranged perpendicular to the movement axis 18 of the piston 16.
- a bore longitudinal axis 58 of the bore 36 is not, as was previously known, also arranged perpendicular to the movement axis 18 of the piston 16, but at an angle to the high ⁇ pressure connection longitudinal axis 54. This angle moves in this case in a range between 1 ° and 10 °, in particular between 2 ° and 8 °, preferably between 4 ° and 6 °. This can do that
- Outlet volume 32 of the high-pressure port 24 are made smaller than would be the case with a perpendicular to the axis of movement 18 arranged bore longitudinal axis 58, so that also acting forces on, for example, a weld 60 of the high pressure port 24 are lower.
- FIG. 3 shows a longitudinal sectional view of the high-pressure fuel pump 10 from FIG. 1 in a detail area of the pressure limiting valve 38 or the bore 36.
- the bore 36 is not only angled horizontally (see FIG the high-pressure connection longitudinal axis 54 is arranged, but also angled perpendicular, so that an angle ß results between bore longitudinal axis 58 and movement axis 18, which moves in a range between 95 ° and 105 °, in particular between 98 ° and 102 °.
- This also makes the outlet volume 32 can be made smaller, so that acting forces are reduced.
- FIG. 4 shows a further longitudinal section in detail in a region of the pressure chamber 14.
- the bore 36 in a preferred embodiment not only has the connection region 46 to the inlet volume 30, but also a connection opening 62 which defines the bore 36 connects directly to the pressure chamber 14.
- the connection opening 62 is arranged in a side wall 64 of the bore 36, which extends parallel to the longitudinal axis 52 of the return spring 48 and thus defines the receiving area 44 for the pressure relief valve 38 with.
- connection opening 62 is present in addition to the connecting portion 46, during the operation of the high-pressure fuel pump 10, a circulation of the fuel can be achieved, whereby the bore 36 can be constantly flushed through and cleaned of dirt.
- connection region 46 has great advantages. parts. Because the normally existing drain hole from the bore 36 into the pressure chamber 14 is usually generated by drilling the pressure chamber 14. This creates an undefined contour that is difficult to deburr on the one hand by the tolerance fluctuations, on the other hand, during further processing of the construction curve such. B. the honing can lead to damage of the components. In addition, there is the disadvantage, if the bore 36 is designed as a blind hole, that particles can collect in the rear region, in particular during the production process (honing), and can block the bore 36. So far, it is known, for example, by specially prepared Spüllanzen that remove the honing slurry with high pressure, the bore 36 rinse.
- connection region 48 which is configured such that the connection opening 62 can be dispensed with.
- connection opening 62 can even be dispensed with the lancet, which can lead to an increase in the process reliability or simplification of the process.
- connection opening 62 is present, a circulation of the cleaning suspension during washing can also be generated in the production process, as a result of which the bore 36 can be rinsed better.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201680047118.7A CN107850027B (zh) | 2015-08-10 | 2016-06-29 | 燃料高压泵 |
KR1020187006547A KR102061986B1 (ko) | 2015-08-10 | 2016-06-29 | 고압 연료 펌프 |
JP2018506827A JP6574048B2 (ja) | 2015-08-10 | 2016-06-29 | 燃料高圧ポンプ |
US15/751,625 US10900451B2 (en) | 2015-08-10 | 2016-06-29 | High-pressure fuel pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015215186.7 | 2015-08-10 | ||
DE102015215186.7A DE102015215186B3 (de) | 2015-08-10 | 2015-08-10 | Kraftstoffhochdruckpumpe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2017025241A1 true WO2017025241A1 (de) | 2017-02-16 |
Family
ID=56292718
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2016/065163 WO2017025241A1 (de) | 2015-08-10 | 2016-06-29 | Kraftstoffhochdruckpumpe |
Country Status (6)
Country | Link |
---|---|
US (1) | US10900451B2 (de) |
JP (1) | JP6574048B2 (de) |
KR (1) | KR102061986B1 (de) |
CN (1) | CN107850027B (de) |
DE (1) | DE102015215186B3 (de) |
WO (1) | WO2017025241A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017211981B3 (de) * | 2017-07-13 | 2018-09-27 | Continental Automotive Gmbh | Kraftstoffeinspritzsystem für eine Brennkraftmaschine |
CN116438375A (zh) | 2020-12-17 | 2023-07-14 | 日立安斯泰莫株式会社 | 燃料泵 |
US11352994B1 (en) * | 2021-01-12 | 2022-06-07 | Delphi Technologies Ip Limited | Fuel pump and combination outlet and pressure relief valve thereof |
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DE10327411A1 (de) * | 2002-10-15 | 2004-04-29 | Robert Bosch Gmbh | Druckbegrenzungsventil sowie Kraftstoffsystem mit einem solchen Druckbegrenzungsventil |
DE102008045730A1 (de) * | 2007-09-07 | 2009-03-19 | GM Global Technology Operations, Inc., Detroit | Kraftstoffeinspritzpumpe mit geringer Rückflusspulsation |
KR20110051826A (ko) * | 2009-11-11 | 2011-05-18 | 현대자동차주식회사 | 고압 연료 펌프의 토출 밸브와 압력 릴리프 밸브 일체형 구조 |
KR20120018395A (ko) * | 2010-08-23 | 2012-03-05 | (주)모토닉 | 직접분사식 가솔린 엔진용 고압연료펌프 |
JP2014136973A (ja) * | 2013-01-15 | 2014-07-28 | Toyota Motor Corp | 高圧燃料ポンプ |
US20150020776A1 (en) * | 2013-07-18 | 2015-01-22 | Denso Corporation | Fuel delivery system containing high pressure pump with isolation valves |
Family Cites Families (20)
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DE3424401A1 (de) * | 1984-07-03 | 1986-01-09 | Robert Bosch Gmbh, 7000 Stuttgart | Gleichdruckventil fuer kraftstoffeinspritzpumpen |
JP3471587B2 (ja) * | 1997-10-27 | 2003-12-02 | 三菱電機株式会社 | 筒内噴射用高圧燃料ポンプ |
DE10118936A1 (de) | 2001-04-18 | 2002-11-07 | Bosch Gmbh Robert | Druckbegrenzungseinrichtung sowie Kraftstoffsystem mit einer solchen Druckbegrenzungseinrichtung |
DE10237593A1 (de) | 2002-08-16 | 2004-03-11 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
ES2256621T3 (es) * | 2002-10-15 | 2006-07-16 | Robert Bosch Gmbh | Valvula de limitacion de presion para un sistema de inyeccion de combustible. |
DE102004013307B4 (de) * | 2004-03-17 | 2012-12-06 | Robert Bosch Gmbh | Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil |
JP4221760B2 (ja) | 2005-01-17 | 2009-02-12 | 株式会社デンソー | 高圧燃料ポンプ |
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DE102008043217A1 (de) | 2008-10-28 | 2010-04-29 | Robert Bosch Gmbh | Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine |
JP2010156256A (ja) | 2008-12-26 | 2010-07-15 | Denso Corp | 高圧ポンプ |
DE102009001465A1 (de) | 2009-03-11 | 2010-09-16 | Robert Bosch Gmbh | Einspritzpumpe zur Versorgung einer Kolbenkraftmaschine mit Treibstoff |
IT1396473B1 (it) * | 2009-03-30 | 2012-12-14 | Magneti Marelli Spa | Pompa carburante con una valvola di massima pressione perfezionata per un sistema di iniezione diretta |
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IT1401819B1 (it) | 2010-09-23 | 2013-08-28 | Magneti Marelli Spa | Pompa carburante per un sistema di iniezione diretta. |
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KR101556637B1 (ko) | 2014-05-21 | 2015-10-02 | 주식회사 현대케피코 | 댐핑 구조를 가지는 내연기관용 고압 펌프 |
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-
2015
- 2015-08-10 DE DE102015215186.7A patent/DE102015215186B3/de active Active
-
2016
- 2016-06-29 KR KR1020187006547A patent/KR102061986B1/ko active IP Right Grant
- 2016-06-29 WO PCT/EP2016/065163 patent/WO2017025241A1/de active Application Filing
- 2016-06-29 CN CN201680047118.7A patent/CN107850027B/zh active Active
- 2016-06-29 JP JP2018506827A patent/JP6574048B2/ja active Active
- 2016-06-29 US US15/751,625 patent/US10900451B2/en active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
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DE10327411A1 (de) * | 2002-10-15 | 2004-04-29 | Robert Bosch Gmbh | Druckbegrenzungsventil sowie Kraftstoffsystem mit einem solchen Druckbegrenzungsventil |
DE102008045730A1 (de) * | 2007-09-07 | 2009-03-19 | GM Global Technology Operations, Inc., Detroit | Kraftstoffeinspritzpumpe mit geringer Rückflusspulsation |
KR20110051826A (ko) * | 2009-11-11 | 2011-05-18 | 현대자동차주식회사 | 고압 연료 펌프의 토출 밸브와 압력 릴리프 밸브 일체형 구조 |
KR20120018395A (ko) * | 2010-08-23 | 2012-03-05 | (주)모토닉 | 직접분사식 가솔린 엔진용 고압연료펌프 |
JP2014136973A (ja) * | 2013-01-15 | 2014-07-28 | Toyota Motor Corp | 高圧燃料ポンプ |
US20150020776A1 (en) * | 2013-07-18 | 2015-01-22 | Denso Corporation | Fuel delivery system containing high pressure pump with isolation valves |
Also Published As
Publication number | Publication date |
---|---|
US20180313314A1 (en) | 2018-11-01 |
CN107850027A (zh) | 2018-03-27 |
JP2018523778A (ja) | 2018-08-23 |
KR20180038505A (ko) | 2018-04-16 |
KR102061986B1 (ko) | 2020-01-02 |
US10900451B2 (en) | 2021-01-26 |
JP6574048B2 (ja) | 2019-09-11 |
CN107850027B (zh) | 2020-09-15 |
DE102015215186B3 (de) | 2016-12-15 |
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