EP3141737A1 - Vanne pour l'ajout de fluide - Google Patents

Vanne pour l'ajout de fluide Download PDF

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Publication number
EP3141737A1
EP3141737A1 EP16179669.3A EP16179669A EP3141737A1 EP 3141737 A1 EP3141737 A1 EP 3141737A1 EP 16179669 A EP16179669 A EP 16179669A EP 3141737 A1 EP3141737 A1 EP 3141737A1
Authority
EP
European Patent Office
Prior art keywords
armature
spring
spring element
valve
radially
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
EP16179669.3A
Other languages
German (de)
English (en)
Other versions
EP3141737B1 (fr
Inventor
Peter Land
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3141737A1 publication Critical patent/EP3141737A1/fr
Application granted granted Critical
Publication of EP3141737B1 publication Critical patent/EP3141737B1/fr
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
    • 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
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • 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
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0685—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature and the valve being allowed to move relatively to each other or not being attached to each other
    • 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
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M63/0075—Stop members in valves, e.g. plates or disks limiting the movement of armature, valve or spring
    • 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
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/006—Springs assisting hydraulic closing force

Definitions

  • the invention relates to a valve for metering a fluid, in particular a fuel injection valve for internal combustion engines. Specifically, the invention relates to the field of injectors for fuel injection systems of motor vehicles, in which there is preferably a direct injection of fuel into combustion chambers of an internal combustion engine.
  • a fuel injector which is used for fuel injection systems of internal combustion engines.
  • the known fuel injection valve comprises a valve needle which cooperates with a valve seat surface to a sealing seat, and an armature connected to the valve needle, which is acted upon by a return spring in a closing direction and which cooperates with a magnetic coil.
  • the anchor is in this case arranged stationarily on the valve needle.
  • valve according to the invention with the features of claim 1 has the advantage that an improved design and operation are possible.
  • a rotational movement of the armature with respect to the valve needle can be prevented.
  • the fluid serving as armature armature is not fixedly connected to the valve needle, but mounted between stops flying.
  • stops can be realized by stop sleeves and / or stop rings.
  • the armature is adjusted in the idle state with respect to the valve needle fixed stop, so that the armature rests there.
  • the complete armature free travel is then available as an acceleration section. This results in comparison with a fixed connection of the armature with the valve needle the advantage that the valve needle can be safely opened even at higher pressures by the resulting pulse of the armature when opening the same magnetic force.
  • Another advantage is that a decoupling of the masses involved takes place so that the resulting impact forces on the sealing seat are divided into two pulses.
  • the spring element can be clamped radially with the armature or a separate spring force transmission means.
  • a clamp on the armature a suitable structural design of the armature is provided. If the spring force transmission means is provided, then there are greater constructive freedom in the design of the armature and the possibility of simplifying the design of the armature.
  • a spring force transmission means may be suitably connected to the armature. Such a connection can be achieved, for example, by welding.
  • the spring force transmission means is not necessarily provided here as an additional element, which is used exclusively for the rotational fixation, since it can also be used for applying the spring force in a suitable direction to the anchor.
  • Possible embodiments according to claim 2 have the advantage that by the shape of the spring element, the clamping can be placed especially on the end regions, in particular on the last or the last turns. Furthermore, contact with other elements can thereby be avoided.
  • the embodiment according to claim 3 has the advantage that a simplification of the design of the armature and / or at least one additional functionality can be realized via the spring force transmission means.
  • a direction reversal of the spring force can be achieved via the spring force transmission means.
  • a guide on the valve needle can be improved via the spring force transmission means.
  • An advantageous development, with which, for example, such a reversal of the spring force direction is possible, is specified in claim 4.
  • a receptacle for the spring element can be created in addition, which allows easy installation.
  • An advantageous attachment for radial clamping is possible in this regard according to claim 5.
  • the spring element can also be clamped radially inwardly on a spring force transmission means.
  • the spring force transmission means can also realize a leadership function.
  • the embodiment according to claim 8 has the advantage that a direct clamping to the anchor is possible. Here, a clamping to the outside can be realized.
  • the development according to claim 9 are variants that allow terminals inwardly or outwardly to the stop element.
  • the holding force can be adjusted by the geometry in the relaxed state and a spring rate.
  • valve needle in claim 10 variants are given, indicating the advantageous embodiments of the valve needle.
  • a separate stop element can in this case be welded onto the valve needle, for example.
  • the two-sided terminals of the spring force transmission means a backlash-free rotational fixation of the armature can be realized.
  • a spring inner diameter for enabling the clamping connection with a shoulder or the like can be selected smaller than a diameter of the heel.
  • the spring element can be rotated counter to its winding direction and pushed simultaneously on the heel or the like. By the rotational movement then increases the spring inner diameter and the paragraph or the like penetrates into the wound spring element until the desired end position is reached. Then hold the spring element by friction on the heel or the like. The holding force is set by the excess of the spring element and the spring rate.
  • the spring outer diameter in the initial state is greater than the bore or the like.
  • the spring element is rotated in its winding direction and simultaneously pushed into the bore or the like. By the rotational movement then reduces the spring outside diameter and the wound spring element penetrates into the bore or the like.
  • Fig. 1 shows a valve 1 in a partial, schematic sectional view according to a first embodiment.
  • the valve 1 serves to meter a fluid.
  • the valve 1 can in this case be designed in particular as a fuel injection valve 1.
  • a preferred application is a fuel injection system in which a plurality of such fuel injection valves 1 are designed as high-pressure injection valves 1 and serve for the direct injection of fuel into associated combustion chambers of the internal combustion engine.
  • liquid or gaseous fuels can be used as the fuel.
  • the valve 1 has an actuator 2, which comprises a magnetic coil 3 and an armature 4.
  • an actuator 2 which comprises a magnetic coil 3 and an armature 4.
  • By energizing the magnetic coil 3 is closed via an inner pole 5 of the actuator 2 and a housing 6, which is at least partially ferromagnetic, a magnetic circuit, whereby an actuation of the armature 4 takes place.
  • actuation of a valve needle 7, which is guided movably along the longitudinal axis 8 in the housing 6, is again possible via the armature 4.
  • the armature 4 is also guided along the longitudinal axis 8.
  • the interaction of the armature 4 with the valve needle 7 takes place here so that between stop elements 9, 10, a relative movement of the armature 4 is made possible to the valve needle 7.
  • the stop elements 9, 10 can in this case be designed as stop rings 9, 10 and / or stop sleeves 9, 10.
  • the armature 4 also has a further end face 13, which faces a stop surface 14 of the stop element 10.
  • the valve needle 7 serves to actuate a valve closing body 15, which may be formed integrally with the valve needle 7.
  • the valve closing body 15 cooperates with a valve seat surface 16 to form a sealing seat.
  • the valve 1 has a spring cup 20, which in this embodiment has a plurality of openings 21, 22 which are circumferentially distributed on the spring cup 20 are configured, wherein for ease of illustration, the openings 21, 22 are marked.
  • the armature 4 has bores 23, 24 which extend coaxially from the further end face 13 to extend the end face 12 and allow a flow of a fluid.
  • the fluid may be, for example, the fuel to be metered, which is supplied via an axial channel 25 and then passes through a space 26 to the valve closing body 15.
  • the spring cup 20 is welded in this embodiment with the armature 4, which is illustrated by a circumferential weld 27.
  • a spring element 28 is arranged, which has a suitable number of turns 29, 30, 31. To simplify the illustration, the turns 29, 31 provided at the ends and a turn 30 provided between these turns 29, 31 are marked here.
  • a shoulder 35 is formed in this embodiment.
  • an inner wall 36 is formed at the spring cup 20 at the spring cup 20 at the spring cup 20, an inner wall 36 is formed.
  • the spring element 28 is clamped on the one hand at least with its last turn 29 on the shoulder 35 of the stop element 9.
  • the last turn 29 is slightly expanded during assembly, so that there is a radial bias.
  • the spring element 28 is clamped against the inner wall 36 of the spring cup 20, at least with its last turn 31.
  • the last turn 31 is slightly compressed during assembly.
  • the spring element 28 is formed in this embodiment so that the last turn 29 is smaller than a diameter of the shoulder 35 and the spring element 28 is thus expanded and thus holds by a frictional engagement on the stop element 9.
  • the winding 31, however, is larger than an inner diameter of the spring cup 20 formed on the inner wall 36, wherein the spring element 28 is screwed during assembly and then holds by a frictional engagement in the spring cup 20.
  • the stop element 10 may be welded onto the valve needle 7, as shown in the Fig. 1 is illustrated by a circumferential weld 37. Accordingly, the stop element 9 can be welded by means of a peripheral weld 38 on the valve needle 7. Here, the anchor free travel over the distance of the stop elements 9, 10 is set.
  • the spring element 28 may be designed in particular conical. Such a conical design is also based on the Fig. 2 illustrated.
  • the valve 1 also has a return spring 39 which acts on the valve needle 7 via the stop element 10.
  • the return spring 39 thus also acts to apply a bias to the sealing seat.
  • the initial position of the armature 4 on the abutment surface 11 is ensured via the spring element 28.
  • the armature 4 by means of the spring cup 20th acted upon by an axial spring force acting counter to an opening direction 40.
  • the complete anchor free travel available.
  • the armature 4 is thus first accelerated so that it can build up a motion impulse. If the armature 4 abuts the stop surface 14 of the stop element 10 after passing through the armature free travel, then a larger momentum impulse is available for opening the valve 1.
  • the movement of the armature 4 with the valve needle 7 is then limited by abutment against the inner pole 5.
  • To close the solenoid 3 is de-energized, so that due to the return spring 39 is closing. About the spring element 28, the armature 4 is returned to its original position at the end.
  • Fig. 2 shows that in Fig. 1 shown valve 1 in a partial, schematic sectional view according to a second embodiment.
  • the spring element 28 is designed as a conically wound spring element 28 with an axially tapering envelope 45.
  • the envelope 45 may be designed as a lateral surface of a truncated cone.
  • the extent of a conical configuration of the spring element 28 depends on the diameter of the shoulder 35 and the inner diameter of the inner wall 36 in the region of the winding 31. It is essential that a sufficient radial clamping is achieved by an expansion of the winding 29 and a compression of the winding 31.
  • Fig. 3 shows the in Fig. 1 labeled III section of a valve 1 according to a third embodiment.
  • an annular recess 46 in the form of an annular groove 46 is formed on the armature 4, in which the spring element 28 is inserted at least with its last turn 29.
  • an outer diameter of the winding 29 is set so large that a radial compression is required to mount the spring element 28.
  • the spring element 28 is then clamped radially in the annular recess 46 of the armature 4 by radial compression.
  • a radial clamping on a shoulder 47 of the stop element 10 is made possible on the stop element 10 by spreading the spring element 28 on its turn 31. At least on the winding 31, the spring element 28 is radially spread.
  • the annular recess 46 is provided in this embodiment on the end face 13 of the armature 4, since the spring element 28 then acts counter to the opening direction 40 to urge the armature 4 in its initial position.
  • Fig. 4 shows the in Fig. 1 labeled III section of a valve 1 according to a fourth embodiment.
  • a shoulder 48 is formed on the armature 4.
  • the end face 13, with which the armature 4 abuts against the stop surface 14 of the stop element 10, is formed in the region of the shoulder 48 in this exemplary embodiment.
  • the winding 31 of the spring element 28 is in a comparable manner as in the case of the Fig. 3 described third embodiment clamped to the paragraph 47.
  • the spring element 28 is clamped in this embodiment, also on the shoulder 48 of the armature 4, wherein the clamping takes place by spreading at least the last turn 29 of the spring element 28.
  • the clamping is thus in this case also on the shoulder 48 radially inwards.
  • the spring element 28 is configured in this embodiment as a belly-shaped coiled spring element 28 having an axially widening and then rejuvenating envelope 45. This avoids that the spring element 28 abuts between its both sides provided last turns 29, 31, for example with the winding 30, to a part of the armature 4 or a part 49 of the stop element 10.
  • the spring element 28 is therefore expanded in this embodiment at both ends or the last turns 29, 31 and holds there by frictional engagement on its partner 47, 48, ie the shoulder 47 of the stop element 10 or the shoulder 48 of the armature. 4
  • Fig. 5 shows the in Fig. 1 III labeled section of a valve 1 according to a fifth embodiment.
  • an annular recess 46 is configured on the armature 4, which, however, in contrast to the annular recess 46 of the armature 4 according to the third embodiment, which is based on the Fig. 3 is described, directly adjacent to the valve needle 7.
  • the annular recess 46 of the armature 4 is therefore designed as an annular step 46.
  • the stop element 10 has an inner wall 51, which is formed on the basis of an annular recess 50 configured on the stop element 10.
  • the annular recess 50 also directly adjoins the valve needle 7.
  • the spring element 28 is now on the one hand at least on the last turn 29 radially clamped by compression of the annular recess 46 to the outside with the armature 5 radially. Accordingly, the spring element 28 on the other hand, at least at the last Winding 31 is clamped by compressing radially outwardly against the inner wall 51 of the stop element 10.
  • the spring element 28 and / or the inner wall 51 and the annular recess 50 of the stop element 10 are designed so that the turns, for example, the winding 30, which lie between the clamped turns 29, 31, preferably no contact on the one hand to the inner wall 51 and on the other hand to the valve needle 7 have.
  • a designed as a spring cup 20 spring force transmission means 20 is provided, to which the spring element is clamped by compression radially.
  • no such spring force transmission means is provided.
  • a sixth exemplary embodiment is described, in which a spring force transmission means 60 designed as a guide sleeve 60 is provided, in which case no reversal of the direction of the force of the spring element 28 takes place.
  • Fig. 6 shows the in Fig. 1 III labeled section of a valve 1 according to a sixth embodiment.
  • a guide sleeve 60 is provided, which is guided on the valve needle 7.
  • the guide is in this case between the abutment surfaces 11, 14 of the stop elements 9, 10.
  • the armature 4 is fixedly connected to the guide sleeve 60 in a suitable manner.
  • This embodiment has the advantage that the manufacture of the armature 4 is simplified, since the guide clearance is given by the pairing with the guide sleeve 60 and the valve needle 7. Furthermore, an axial length of the guide sleeve 60 can be shortened in a simple manner to the required extent.
  • the guide sleeve 60 has a shoulder 61, with which the guide sleeve 60 protrudes axially beyond the end face 13 of the armature 4.
  • the spring element 28 is clamped radially with its last turn 29.
  • a belly-shaped configuration of the spring element 28 is predetermined, as it is also based on the Fig. 4 described fourth embodiment is the case.
  • the clamping on the stop element 10 may also be based on the Fig. 4 correspond described embodiment.
  • An axial through-hole 62 of the armature 4 can thus be used directly for guiding on the valve needle 7, depending on the design of the valve 1, or also allow the attachment to a spring force transmission means 60 designed as a guide sleeve 60.
  • the spring element 28 can transmit its spring force required for the return directly or by means of a spring force transmission means 20, 60 to the armature 4, wherein a support on one of the stop elements 9, 10 takes place.
  • a plurality of such spring elements 28 are provided, which in sum the apply required restoring force.
  • a guide sleeve 60 may extend completely through the axial throughbore 62 of the armature 4. In such an embodiment, the stop on the stop surfaces 11, 14 carried on the guide sleeve 60 respectively.
  • a modified embodiment is conceivable in which on the one hand a stop on the armature 4 and on the other hand on the guide sleeve 60 takes place.
  • stop elements 9, 10 are not necessarily designed as separate components. Specifically, one of the stop elements 9, 10 may also be designed in one piece with the valve needle 7.
  • the spring element 28 is in this case on the one hand radially clamped with the armature 4 or a spring force transmission means 20, 60 and on the other hand radially with the relevant stop element 9, 10. This jamming takes place on both sides preferably in such a manner that a backlash-free rotational fixation of the armature 4 is realized.

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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)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Magnetically Actuated Valves (AREA)
EP16179669.3A 2015-09-14 2016-07-15 Vanne pour l'ajout de fluide Not-in-force EP3141737B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015217516.2A DE102015217516A1 (de) 2015-09-14 2015-09-14 Ventil zum Zumessen eines Fluids

Publications (2)

Publication Number Publication Date
EP3141737A1 true EP3141737A1 (fr) 2017-03-15
EP3141737B1 EP3141737B1 (fr) 2018-03-07

Family

ID=56413562

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16179669.3A Not-in-force EP3141737B1 (fr) 2015-09-14 2016-07-15 Vanne pour l'ajout de fluide

Country Status (3)

Country Link
EP (1) EP3141737B1 (fr)
KR (1) KR20170032200A (fr)
DE (1) DE102015217516A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111344483A (zh) * 2017-11-22 2020-06-26 日立汽车系统株式会社 燃料喷射装置
CN111810332A (zh) * 2019-04-12 2020-10-23 罗伯特·博世有限公司 用于配量流体的阀

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016220326A1 (de) * 2016-10-18 2018-04-19 Robert Bosch Gmbh Ventil zum Zumessen eines gasförmigen oder flüssigen Kraftstoffs

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10360330A1 (de) 2003-12-20 2005-07-21 Robert Bosch Gmbh Brennstoffeinspritzventil
US20070114299A1 (en) * 2005-11-02 2007-05-24 Martin Scheffel Fuel injector
WO2013085140A1 (fr) * 2011-12-09 2013-06-13 주식회사 케피코 Injecteur de carburant à injection directe
DE102013223458A1 (de) * 2013-11-18 2015-05-21 Robert Bosch Gmbh Ventil zum Zumessen von Fluid

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10360330A1 (de) 2003-12-20 2005-07-21 Robert Bosch Gmbh Brennstoffeinspritzventil
US20070114299A1 (en) * 2005-11-02 2007-05-24 Martin Scheffel Fuel injector
WO2013085140A1 (fr) * 2011-12-09 2013-06-13 주식회사 케피코 Injecteur de carburant à injection directe
DE102013223458A1 (de) * 2013-11-18 2015-05-21 Robert Bosch Gmbh Ventil zum Zumessen von Fluid

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111344483A (zh) * 2017-11-22 2020-06-26 日立汽车系统株式会社 燃料喷射装置
CN111344483B (zh) * 2017-11-22 2022-03-08 日立安斯泰莫株式会社 燃料喷射装置
US11591994B2 (en) 2017-11-22 2023-02-28 Hitachi Astemo, Ltd. Fuel injection device
CN111810332A (zh) * 2019-04-12 2020-10-23 罗伯特·博世有限公司 用于配量流体的阀

Also Published As

Publication number Publication date
DE102015217516A1 (de) 2017-03-16
KR20170032200A (ko) 2017-03-22
EP3141737B1 (fr) 2018-03-07

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