EP3508714A1 - Piston pour un moteur à combustion interne - Google Patents

Piston pour un moteur à combustion interne Download PDF

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Publication number
EP3508714A1
EP3508714A1 EP19150136.0A EP19150136A EP3508714A1 EP 3508714 A1 EP3508714 A1 EP 3508714A1 EP 19150136 A EP19150136 A EP 19150136A EP 3508714 A1 EP3508714 A1 EP 3508714A1
Authority
EP
European Patent Office
Prior art keywords
piston
inlet
channel
cooling
cooling fluid
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
EP19150136.0A
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German (de)
English (en)
Other versions
EP3508714B1 (fr
Inventor
Christoph Zelzer
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.)
MAN Truck and Bus SE
Original Assignee
MAN Truck and Bus SE
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
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Application filed by MAN Truck and Bus SE filed Critical MAN Truck and Bus SE
Publication of EP3508714A1 publication Critical patent/EP3508714A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F02F3/16—Pistons  having cooling means
    • F02F3/20—Pistons  having cooling means the means being a fluid flowing through or along piston
    • F02F3/22—Pistons  having cooling means the means being a fluid flowing through or along piston the fluid being liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/06—Arrangements for cooling pistons
    • F01P3/10—Cooling by flow of coolant through pistons

Definitions

  • the invention relates to a piston for an internal combustion engine.
  • a piston For cooling a piston of an internal combustion engine, a piston may have an internal piston cooling channel.
  • the piston cooling passage may have an inlet at a bottom of the piston. Through the inlet, cooling fluid, for example, oil injected from a cooling fluid injection nozzle in a direction toward the inlet, may enter the piston cooling passage. The cooling fluid may exit the piston cooling passage through an outlet at the bottom of the piston.
  • a liquid-cooled piston for internal combustion engines which has an at least partially annular segment-shaped cooling channel.
  • the cooling channel is formed below a piston crown in a piston upper part.
  • the cooling channel has openings for the inlet and outlet of the cooling liquid. The openings are formed with a drogue.
  • a piston in which an inlet channel for a piston cooling channel is arranged completely in a piston shaft of a piston.
  • the inlet channel has a funnel-shaped inlet region.
  • the invention is based on the object to improve a cooling fluid supply to a piston cooling channel.
  • sufficient cooling fluid should be supplied to the piston cooling channel of the piston even at high piston speeds.
  • the piston is suitable for an internal combustion engine (eg reciprocating internal combustion engine).
  • the piston has an inner piston cooling channel for cooling the piston.
  • the piston has an inlet channel, which opens into the piston cooling channel on.
  • a flow cross section the inlet channel tapers in a direction to the inlet of the inner piston cooling channel at least in sections, in particular funnel-shaped.
  • the inlet passage is in addition to promoting (eg, enhancing, increasing) cooling fluid flow (eg, reducing cooling fluid friction losses) to the inlet of the internal piston cooling passage.
  • the cooling fluid may be oil.
  • the inlet channel may include means (eg, surface treatment, coating, and / or flow guide member (s)) for promoting cooling fluid flow to the piston cooling channel.
  • means eg, surface treatment, coating, and / or flow guide member (s) for promoting cooling fluid flow to the piston cooling channel.
  • the tapered inlet passage intensively directs injected cooling fluid to the inlet of the piston cooling passage.
  • the cooling fluid passes in terms of quantity reinforced in the cooling fluid channel and can better carry away the heat load occurring and thus reduce a temperature of the piston.
  • a flow of cooling fluid through the inlet channel into the inlet of the cooling fluid channel can be promoted.
  • the inlet channel may be arranged below an underside of the piston.
  • the inlet channel can be arranged directly below an inlet of the piston cooling channel.
  • the inlet of the piston cooling channel opens in a lower side of the piston.
  • the cooling fluid channel may be annular and / or may have a plurality of subchannels. It is possible that the cooling fluid channel is arranged below a piston crown in a piston upper part.
  • the piston cooling channel may have an outlet.
  • the outlet may be arranged with respect to a center axis of the piston opposite to the inlet of the cooling fluid channel.
  • the inlet channel for conveying the cooling fluid flow in the inlet channel is at least partially surface-treated, in particular for reducing a surface roughness.
  • the inlet channel may be polished his. This cooling fluid friction losses can be reduced in the inlet channel and thus a cooling fluid flow can be increased in the cooling fluid channel.
  • a peripheral surface of the inlet channel may be surface-treated at least in sections, in particular for reducing a surface roughness of the peripheral surface.
  • the peripheral surface may be at least partially polished.
  • the inlet channel for conveying the cooling fluid flow in the inlet channel is coated with a flow resistance-reducing and / or a surface roughness-reducing coating.
  • the coating may be applied by thermal spraying.
  • a circumferential surface of the inlet channel may be coated at least in sections.
  • the inlet channel for conveying the cooling fluid flow in the inlet channel comprises at least one flow guide element for guiding the cooling fluid in a direction to the inlet of the inner piston cooling channel.
  • the cooling fluid can be directed to the inlet of the inner piston cooling channel.
  • the cooling fluid can flow faster into the cooling fluid channel.
  • a cooling fluid flow into the cooling fluid channel can be increased.
  • the at least one flow guide element is designed as a groove in a peripheral surface of the inlet channel.
  • the at least one flow guide element is designed as a projection, in particular as a guide fin, on a peripheral surface of the inlet channel.
  • the groove and / or the protrusion may be rounded (eg with a radius between 0.1 mm and 5 mm) or square (eg rectangular, trapezoidal, etc.).
  • the groove and / or the projection may have a width between 0.1 mm and 5 mm.
  • a side surface of an angular groove and / or an angular projection may include an angle in a range between 0 ° and 90 ° with a normal of the peripheral surface.
  • the at least one flow guide element may have a height or depth in a range between 0.1 mm and 5 mm.
  • the at least one flow guide element extends in a direction toward the inlet of the inner piston cooling channel. It is also possible for the at least one flow-guiding element to extend in a straight-line and / or at least partially helical manner at least in sections. Thus, the cooling fluid can be supplied in a straight line or helical to the inlet of the inner cooling fluid channel.
  • the at least one flow guide element has a plurality of, in particular symmetrical, flow guide elements arranged around a circumference of the inlet channel.
  • the at least one flow guide element can be pressed, cut or incorporated in a peripheral surface of the inlet channel.
  • the inlet channel is at least partially formed by a drogue, which is connected to an underside of the piston.
  • the drogue is integrally formed integrally with the underside of the piston or formed separately and connected to the bottom, in particular detachably connected.
  • the drogue and the underside of the piston are made of the same material or of different materials. This can be used, for example, cost-effective materials and / or easily moldable or machinable materials for the drogue.
  • the drogue may have a height greater than 0 mm and / or less than 60 mm, in particular in a range between 5 mm and 40 mm.
  • the drogue is at least partially formed by a piston skirt.
  • the piston skirt form a wall segment of the drogue, which is connected to a further, formed separately from the piston skirt wall segment of the drogue.
  • the inlet channel tapers at least in sections at an angle greater than 0 ° and / or less than 45 °, in particular between 5 ° and 30 ° a longitudinal axis of the inlet channel.
  • the inlet channel opens rounded into the inlet of the piston cooling channel, in particular with a radius greater than 0 mm and / or smaller than 30 mm, preferably between 5 mm and 20 mm.
  • the invention also relates to a cooling fluid injector configured to inject the cooling fluid with a swirl (eg, helical flow and / or rotation about an axis of the cooling fluid jet).
  • the swirl can stabilize the cooling fluid jet injected in a direction toward an underside of a piston.
  • the thus stabilized cooling fluid jet is less affected by spray and Panschfluid in crankcase.
  • the cooling fluid flow supplied to a cooling fluid passage of the piston can be increased in volume.
  • the cooling fluid injector may be included in a device having a piston as disclosed herein.
  • the cooling fluid injector may be directed to an inlet port of the inlet channel.
  • the cooling fluid injection device may be attached to a crankcase of the internal combustion engine, in particular fixed. It is possible for the cooling fluid injector to be fluidly connected to a cooling fluid pump that delivers cooling fluid to the cooling fluid injector.
  • the cooling fluid injection device has an injection nozzle with at least one swirl element, in particular a helical groove and / or a helical projection which is designed to impart a twist to the cooling fluid.
  • the at least one swirl element can be pressed, cut or incorporated in a channel of the injection nozzle.
  • the invention is also directed to a motor vehicle, in particular a utility vehicle, having a piston as disclosed herein or a device as disclosed herein.
  • piston and / or the device as disclosed herein for passenger cars, large engines, off-highway vehicles, stationary engines, marine engines, and so on.
  • the FIG. 1 shows purely schematically an underside of a piston 10.
  • the piston 10 may in an internal combustion engine, for example, a motor vehicle, in particular commercial vehicle, includes his.
  • the commercial vehicle may preferably be a truck or a bus.
  • the piston 10 has two piston pin bosses 12, 14.
  • the piston pin bosses 12, 14 serve to receive a piston pin (not shown).
  • the piston pin connects the piston 10 articulated, in particular pivotally, with a connecting rod (not shown).
  • the piston 10 also has an inlet channel 16.
  • the inlet channel 16 opens into an inlet 28 of an internal piston cooling channel 20 (see FIG. 2 ).
  • the inlet channel 16 and an outlet 18 of the piston cooling channel 20 may be arranged opposite each other with respect to a central longitudinal axis of the piston 10.
  • Intake passage 16 is configured to supply a cooling fluid, for example, oil, to an inlet 28 of inner piston cooling passage 20.
  • the piston cooling passage 20 extends inside the piston 10. Cooling fluid in the piston cooling passage 20 cools the piston 10 during operation from the inside. In order to ensure sufficient cooling of the piston 10 at different piston speed, sufficient cooling fluid must be supplied via the inlet channel 16 to the piston cooling channel 20.
  • the outlet 18 serves to discharge the cooling fluid from the piston cooling passage 20, for example into a crank chamber of the internal combustion engine.
  • FIG. 2 shows an eccentric section through the piston 10 in the region of the inlet channel 16.
  • the inlet channel 16 is partially formed in a drogue 22.
  • the drogue 22 is formed on an underside 24 of the piston 10. It may also be possible to manufacture the drogue 22 as a separate component and, for example, releasably connect it to a bottom 24 of the piston 10.
  • the drogue 22 may be made of the same material as the piston 10 or of another material.
  • the drogue 22 may be partially formed by a portion of a piston shaft 26.
  • the drogue 22 may for example have an axial extent parallel to the piston center axis or height H of less than 60 mm, in particular in a range between 5 mm and 40 mm.
  • the height H may be measured from the bottom 24 of the piston 10.
  • An inlet opening of the inlet channel 16 has a larger flow cross-section than an outlet opening of the inlet channel 16.
  • the inlet channel 16 opens with its outlet opening into an inlet 28 of the piston cooling channel 20.
  • the inlet channel 16 tapers in FIG Catching horn 22 in a direction to the piston cooling passage 20.
  • a peripheral surface 30 may include an acute angle (taper angle) ⁇ with a central longitudinal axis of the intake port 16.
  • the taper angle ⁇ can in particular be greater than 0 ° and less than 45 °, in particular between 5 ° and 30 °.
  • the enlarged inlet opening of the inlet channel 16 allows an increased degree of capture of cooling fluid injected from a cooling fluid injector 32 in a direction toward the drogue 22.
  • the drogue 22 protects cooling fluid within the intake passage 16 from splash and swirl fluid, for example, oil thrown from the crankshaft toward the piston 10, for example. Thus, the cooling fluid within the inlet channel 16 is less affected.
  • FIG. 3 shows an alternative embodiment in which the drogue 22 'is formed so that the inlet channel 16 opens along its entire circumference with a radius R in the inlet 28 of the piston cooling passage 20.
  • the radius R may for example be less than 30 mm, in particular between 5 mm and 20 mm.
  • the drogue 22 'of the embodiment according to FIG. 3 may have a height corresponding to the height H of the drogue 22 of the embodiment FIG. 2 equivalent.
  • the drogue 22 'of the embodiment according to FIG. 3 a taper angle corresponding to the taper angle ⁇ of the embodiment FIG. 2 equivalent.
  • the present application is directed to promoting a flow of cooling fluid within the intake passage 16 in a direction toward the piston cooling passage 20.
  • the inlet channel 16 and / or the cooling fluid injector 32 may be specially configured as described below by way of example.
  • the surface of the peripheral surface 30 of the intake passage 16 may be treated.
  • the treatment may cause a reduction in surface roughness of the peripheral surface 30.
  • the surface of the peripheral surface 30 can be smoothed and thus a cooling fluid friction of cooling fluid flowing along the peripheral surface 30 in a direction to the piston cooling passage 20 can be reduced.
  • the peripheral surface 30 may be polished at least in sections.
  • the peripheral surface 30 of the inlet channel 16 is at least partially coated to reduce cooling fluid friction within the inlet channel 16.
  • the peripheral surface 30 may be coated with a coating which reduces the flow resistance of the cooling fluid and / or reduces a surface roughness of the peripheral surface 30.
  • the coating may be, for example, a paint. It is also possible that the coating is applied, for example, by thermal spraying.
  • FIGS. 4 and 5 show a further embodiment for conveying the cooling fluid flow in the inlet channel 16.
  • the inlet channel 16 a plurality of flow guide elements 34.
  • the flow guide elements 34 are arranged symmetrically around a circumference of the inlet channel 16, for example.
  • the flow guide elements 34 are straight.
  • the flow guide elements 34 may extend completely or in sections between an inlet opening of the inlet channel 16 and an outlet opening of the inlet channel 16, which opens into the inlet 28.
  • the flow guide elements 34 may help to guide the cooling fluid injected into the inlet channel 16 in a direction toward the inlet 28. It is also possible that more or less than the illustrated flow guide elements 34 are provided.
  • the flow guide elements 34 may be formed as, in particular rounded depressions / grooves in the peripheral surface 30. As shown in FIG. 9, the flow guide elements 34 can alternatively or additionally also be formed as, in particular rounded, projections on the peripheral surface 30.
  • a radius K of the flow guide elements 34 may be, for example, between 0.1 mm and 5 mm.
  • the flow guide elements 34 as rectangular, in particular rectangular or trapezoidal, recesses in the peripheral surface 30 (see FIG. 10 ) and / or as angular, in particular rectangular or trapezoidal, projections on the peripheral surface 30 (see FIG. 11 ) are formed.
  • the flow guide elements 34 designed as depressions and / or projections may have, for example, a width B of between 0.1 mm and 5 mm, for example as shown in FIGS FIGS. 10 and 11 is shown.
  • the side walls of the angular flow guide elements 34 may include an angle ⁇ with a normal of the peripheral surface 30 which is, for example, greater than or equal to 0 ° and / or less than or equal to 90 °.
  • the flow guide elements 34, 36 have a height or depth V, which is for example in a range between 0.1 mm and 5 mm.
  • the FIGS. 6 and 7 show another further embodiment for promoting the cooling fluid flow through the inlet channel 16.
  • the inlet channel 16 has a plurality of flow guide elements 36.
  • the flow guide elements 36 are arranged symmetrically around a circumference of the inlet channel 16, for example.
  • the flow guide elements 36 are helically (helically) formed about a central longitudinal axis of the inlet channel 16.
  • the flow guide elements 36 may extend completely or in sections between an inlet opening of the inlet channel 16 and an outlet opening of the inlet channel 16, which opens into the inlet 28. Similar to the flow guide elements 34 according to the embodiment of the FIGS. 4 and 5
  • the flow guide elements 36 may help to direct the cooling fluid injected into the inlet channel 16 in a direction toward the inlet 28. It is also possible that more or less than the illustrated flow guide elements 36 are provided.
  • the flow guiding elements 36 may be in the form of, in particular rounded or angular, recesses in the peripheral surface 30 (see FIG FIGS. 8 and 10 ) and / or as, in particular rounded or angular, projections or protrusions on the peripheral surface 30 (see FIGS. 9 and 11 ) be formed.
  • cooling fluid flow in the inlet channel 16 by combining a surface treatment, a coating, at least one flow guide elements 34 and / or at least one flow guide elements 36.
  • the cooling fluid injector 32 may also be specially designed, as in FIGS FIGS. 2, 3 . 5 and 7 is shown by way of example.
  • the cooling fluid injector 32 may include an injector 38.
  • the injection nozzle 38 may be formed so that upon injection of the cooling fluid, a swirl is imparted to the cooling fluid. As a result, the injection jet can be stabilized and less susceptible to distractions caused by splash and panschfluid.
  • the injection nozzle 38 may be provided with at least one helically shaped swirl element 40 in order to impart a swirl to the cooling fluid during injection.
  • the swirl elements 40 may be formed, for example, as depressions and / or as protrusions in the injection nozzle 38.
  • the invention is not limited to the preferred embodiments described above. Rather, a variety of variants and modifications is possible, which also make use of the inventive idea and therefore fall within the scope.
  • the invention also claims protection of the subject matter and the features of the subclaims independently of the claims referred to.
  • the features of independent claim 1 are independently disclosed.
  • the features of the dependent claims are also disclosed independently of all the features of independent claim 1 and, for example, independently of the features relating to the presence and / or the configuration of the piston, the cooling fluid channel and / or the inlet channel of independent claim 1.
  • the design of the cooling fluid injector is also disclosed regardless of the presence and / or configuration of the piston.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
EP19150136.0A 2018-01-09 2019-01-03 Piston pour un moteur à combustion interne Active EP3508714B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102018100336.6A DE102018100336A1 (de) 2018-01-09 2018-01-09 Kolben für eine Brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP3508714A1 true EP3508714A1 (fr) 2019-07-10
EP3508714B1 EP3508714B1 (fr) 2022-03-30

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ID=64959205

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19150136.0A Active EP3508714B1 (fr) 2018-01-09 2019-01-03 Piston pour un moteur à combustion interne

Country Status (2)

Country Link
EP (1) EP3508714B1 (fr)
DE (1) DE102018100336A1 (fr)

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007315244A (ja) * 2006-05-24 2007-12-06 Toyota Industries Corp 内燃機関のピストン冷却装置
DE202006020280U1 (de) * 2006-11-28 2008-02-21 Ks Kolbenschmidt Gmbh Kühlkanalkolben
EP1925805A1 (fr) * 2006-11-28 2008-05-28 KS Kolbenschmidt GmbH Canal de refroidissement variable pour un piston
DE102011106379A1 (de) * 2011-07-04 2013-01-10 Mahle International Gmbh Kolben für einen Verbrennungsmotor
KR20140023602A (ko) * 2012-08-16 2014-02-27 현대자동차주식회사 오일 갤러리의 냉각 기능 향상을 위한 원통형 회전 구조물을 갖춘 피스톤
DE102012211060A1 (de) * 2012-06-27 2014-04-17 Bayerische Motoren Werke Aktiengesellschaft Kolben für eine Hubkolben-Brennkraftmaschine
CN203835518U (zh) * 2014-02-28 2014-09-17 北汽福田汽车股份有限公司 一种冷却液喷嘴总成及发动机
KR20150099102A (ko) * 2014-02-21 2015-08-31 두산인프라코어 주식회사 엔진의 피스톤
WO2016171004A1 (fr) * 2015-04-23 2016-10-27 日立オートモティブシステムズ株式会社 Piston de moteur à combustion interne et procédé de traitement de surface pour piston de moteur à combustion interne
DE102017113014A1 (de) * 2016-06-13 2017-12-14 Ks Kolbenschmidt Gmbh Kühlkanalöffnung durch Zirkularfräsoperation

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Publication number Priority date Publication date Assignee Title
DE19736135C1 (de) 1997-08-20 1998-10-29 Daimler Benz Ag Flüssigkeitsgekühlter Kolben für Verbrennungsmotoren
JP2005048650A (ja) * 2003-07-28 2005-02-24 Nissan Diesel Motor Co Ltd 内燃機関用ピストン
DE102008035698A1 (de) 2008-07-30 2010-02-04 Mahle International Gmbh Verfahren zur Herstellung eines Kolbens oder Kolbenteils
KR101417117B1 (ko) 2008-10-22 2014-08-07 두산인프라코어 주식회사 피스톤 냉각 장치
KR20150121239A (ko) * 2013-03-05 2015-10-28 페더럴-모걸 코오포레이숀 카본 디포짓 방지 코팅을 지닌 피스톤 및 그 구성 방법
DE102014219821A1 (de) 2014-09-30 2016-03-31 Siemens Aktiengesellschaft Rückführstufe
DE102015002322A1 (de) * 2015-02-26 2016-09-01 Mahle International Gmbh Kolben für einen Verbrennungsmotor

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007315244A (ja) * 2006-05-24 2007-12-06 Toyota Industries Corp 内燃機関のピストン冷却装置
DE202006020280U1 (de) * 2006-11-28 2008-02-21 Ks Kolbenschmidt Gmbh Kühlkanalkolben
EP1925805A1 (fr) * 2006-11-28 2008-05-28 KS Kolbenschmidt GmbH Canal de refroidissement variable pour un piston
DE102011106379A1 (de) * 2011-07-04 2013-01-10 Mahle International Gmbh Kolben für einen Verbrennungsmotor
DE102012211060A1 (de) * 2012-06-27 2014-04-17 Bayerische Motoren Werke Aktiengesellschaft Kolben für eine Hubkolben-Brennkraftmaschine
KR20140023602A (ko) * 2012-08-16 2014-02-27 현대자동차주식회사 오일 갤러리의 냉각 기능 향상을 위한 원통형 회전 구조물을 갖춘 피스톤
KR20150099102A (ko) * 2014-02-21 2015-08-31 두산인프라코어 주식회사 엔진의 피스톤
CN203835518U (zh) * 2014-02-28 2014-09-17 北汽福田汽车股份有限公司 一种冷却液喷嘴总成及发动机
WO2016171004A1 (fr) * 2015-04-23 2016-10-27 日立オートモティブシステムズ株式会社 Piston de moteur à combustion interne et procédé de traitement de surface pour piston de moteur à combustion interne
DE102017113014A1 (de) * 2016-06-13 2017-12-14 Ks Kolbenschmidt Gmbh Kühlkanalöffnung durch Zirkularfräsoperation

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Publication number Publication date
EP3508714B1 (fr) 2022-03-30
DE102018100336A1 (de) 2019-07-11

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