WO2015039653A1 - Verrouillage multiple d'un déphaseur d'arbre à cames et procédé pour faire fonctionner un déphaseur d'arbre à cames - Google Patents

Verrouillage multiple d'un déphaseur d'arbre à cames et procédé pour faire fonctionner un déphaseur d'arbre à cames Download PDF

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Publication number
WO2015039653A1
WO2015039653A1 PCT/DE2014/200321 DE2014200321W WO2015039653A1 WO 2015039653 A1 WO2015039653 A1 WO 2015039653A1 DE 2014200321 W DE2014200321 W DE 2014200321W WO 2015039653 A1 WO2015039653 A1 WO 2015039653A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
hydraulic
locking
stator
camshaft adjuster
Prior art date
Application number
PCT/DE2014/200321
Other languages
German (de)
English (en)
Inventor
Dirk Heintzen
Michael Busse
Gerhard Scheidig
Original Assignee
Schaeffler Technologies Gmbh & Co. Kg
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 Schaeffler Technologies Gmbh & Co. Kg filed Critical Schaeffler Technologies Gmbh & Co. Kg
Publication of WO2015039653A1 publication Critical patent/WO2015039653A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34463—Locking position intermediate between most retarded and most advanced positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34466—Locking means between driving and driven members with multiple locking devices

Definitions

  • the invention relates to etnen hydraulic camshaft adjuster of the vane type, with a stator and with a rotor rotatably in normal operation rotatably arranged therein, the rotor and the stator arranged between them, at least two separate by a rotor-fixed wings workrooms.
  • working chambers formed by a hydraulic power supply device such as an oil pump
  • hydraulic fluid such as oil
  • a camshaft phaser for a camshaft in a motor vehicle such as a car for a truck or a similar commercial vehicle, is already known with a combustion engine.
  • the invention also relates to a method for locking a rotor of a hydraulic camshaft adjuster relative to a stator of the camshaft adjuster.
  • Previous center locking concepts or end stop concepts always allow only a defined starting position. In modern internal combustion engines / engines, however, depending on the starting state of the engine, different starting positions may be necessary, which was previously not possible or not possible. While it was previously known, either in an early or a late or intermediate position, namely the central vegetation. ertion. verTiegeln the camshaft adjuster, should now at least two or better three locking positions can be achieved An appropriate Anateu réelle is also desired
  • a camshaft adjuster is to be made available which, in the starting position, controlled by the control electronics of the engine, can assume a desired of at least two locking positions.
  • the active pressure accumulator is arranged below an axis of rotation of a camshaft which can be connected to the rotor.
  • the term “below” means such an arrangement, which is defined by gravity.
  • the active pressure accumulator has a storage space for hydraulic means, such as oil, which can be made smaller, for example by means of a deformable piston, from which the hydraulic medium can be brought into the interior of a rotor via a pressure medium line. for example, through the interior of the camshaft
  • an outlet of the storage space, and preferably also the storage space itself, below an output of the pressure medium line, approximately below a lower edge of the camshaft, in particular in the region of the supply of the hydraulic fluid to the camshaft, arranged in this way can be a breather of the active pressure accumulator can be prevented and forced a quick start of the adjustment kinematics
  • the storage space has a volume V t , which is greater than the volume Vmung the line route from the outlet of the storage space to the workrooms plus the volume V v cr> o * r ** r of the work spaces is in this way is ensured that there is always enough oil for a rotation of the rotor relative to the stator or the Vemegelungspm- retract-Verhindem, even if the internal combustion engine is not running
  • the oil line between the active accumulator and the adjuster should be as short as possible, since a low Volume of oil that makes the line faster to fill. For the rest of the lubrication system, the line should be isolated during engine startup. Z B by means of a check valve in the actual inflow.
  • a central valve is inserted into the rotor through which hydraulic means of the active pressure accumulator the work spaces and / or designed for receiving the locking pin backdrop can be fed.
  • a rotation of the rotor can be forced thereby and on the other hand a skipping of a locking position, such as the center locking position.
  • a skipping of a locking position such as the center locking position.
  • one of these locking pms is mounted so that it can be retracted into a further link, wherein the links are separated from one another.
  • This further backdrop can be a late-locking link or a spring-locking link, ie a late-locking position or an early-locking position.
  • the center locking position is also understood as MLP (Mtdiock position), wherein the position determined by the Spötverriegelungsposition as a retarded position
  • MLP Meltdiock position
  • the Early Node Position can also be referred to as Advance Position
  • An advantageous embodiment is characterized in that the rotor rotates relative to the stator in an early and / or late and / or middle position over the locking pins can be fixed.
  • the rotor in a rotated at least 5 degrees from the Spatposition position on the stator is rotatably locked or locked
  • the invention also relates to a method for locking a rotor of a hydraulic camshaft adjuster relative to a stator of the camshaft adjuster, wherein at least one locking pin of the rotor to the stator in a center position and additionally in an early or Spatposition is lockable and a hydraulic means of one for filling used by working chambers between the rotor and the stator hydraulic means supply separate active pressure accumulator for acting on a longitudinal movement of the locking pin is used
  • the hydraulic means of the active pressure memory is used to act on a rotational movement of the rotor and / or to prevent the retraction of the locking pin or multiple locking pins in a Mrttenvemegelungskulisse.
  • a camshaft phaser design is presented, which allows two or more locking positions, and a strategy presented in the engine control unit, which allows by using an active pressure accumulator a change in position at engine start. Unlocking problems, such as occur with cam phasers that use a single conical pin, are prevented.
  • the use of two Verriegelungspms is advantageous, even if there is always a minimum game remains.
  • the locking pins can be distributed over the circumference.
  • the locking pins should not face each other by exactly 180 degrees, as otherwise disadvantages would occur if the locking play is too great. This is due to the fact that the manufacturing tolerances add up. Nevertheless, the two nailing pins should at least have a certain absorbency from each other over the circumference.
  • One of these two locking pms can continue to lock into a locking lip which lies at the late stop of the adjustment range, or alternatively, the other locking pin can lock into a locking slide which lies at the early stop of the adjustment range.
  • the supply of hydraulic fluid, for example the oil supply, to the center locking linkage is controlled by a 5/5-way valve.
  • the oil supply to the late-locking mechanism is controlled by a so-called A-chamber of the phaser. This would also be possible for the locking procedure in the morning, as well as the supply from a B-chamber.
  • a change in locking position either from the center to Spat / Early or late / early in the Milte to enable the invention uses an active accumulator, which is started so. that it can store Motoröt during a longer standstill phase and is unlocked at engine start, allowing this stored ötvolumen the activation of the release in one position and the movement to the other position
  • the pressure accumulator should be located below the camshaft axis 9ein and should lead all supply and discharge lines from above to the accumulator to prevent draining the Dnjck Itemss.
  • the volume of the accumulator must be chosen so that enough oil remains to fill the empty working chamber chambers (variable camshaft phaser chambers) and their supply channels, to compensate for leaks and to allow at least one uncompleted adjustment. Is the active accumulator below a supply range of one camshaft adjuster. in particular a camshaft, present, can be dispensed with seals, which at standstill of the combustion engine, the oil does not escape at the same point and the active pressure accumulator does not run idle.
  • connection of the locking pin detent recesses with a " normal " C-oil channel can be released by a valve.
  • the accumulator is capable of being charged by the engine oil system and can be connected or disconnected by an electrical control system. It can be a ballast valve can be used, which can switch on and off the controlled by the control system of Nockenweltenverstellers for controlling the locking pin oil flow.
  • a replacement of an electric camshaft adjuster can be achieved, which reduces the costs in relation to this many times.
  • Efficient camshaft adjusters can now be produced in large numbers and used on internal combustion engines.
  • FIG. 1 shows the arrangement of an active pressure accumulator in a hydraulic camshaft adjuster according to the invention in a longitudinal piston representation
  • Figure 2 shows the shading of a 5/5-way valve with two Ulkammem that form a durcn a wing divided pressure chamber.
  • Figure 3 shows the shading of Figure 2, but with the wing m a
  • Figure 4 is a volume flow / elektnscher control flow diagram, which is the control of the 5/5-way valve. as used in the exemplary embodiment of Figure 2.
  • 5 is a perspective view of a central valve used in the hydraulic camshaft adjuster according to the invention
  • FIG. 6 shows a hydraulic circuit flow and electrical control current diagram.
  • FIG. 7 is a general diagram composed of three sub-diagrams for an emergency locking strategy at stop of FIG. 4, similar to the diagram from FIG. 4, which is used to supply oil to the centrate valve of FIG.
  • FIG. 8 is a comparable to Figure 7 representation of an overall diagram, but with the engine does not cool and a usual start-stop recovery situation is present, wherein a reached in the internal combustion engine stopping center locking position is resolved and the start of a late locking position is preselected
  • FIGS. 9 to 12 show the transition from an advanced position to a late-locking position, passing over a center locking position at engine start
  • FIGS Figures 13 to 16 show the sequence of stopping the engine in an early position and bringing the rotor into a center control position for the restart of the internal combustion engine
  • FIG. 1 shows a first embodiment of a hydraulic camshaft adjusting device 1 according to the invention.
  • the camshaft adjuster is one such hydraulic camshaft adjuster.
  • Is of the wing cell type Is that is, a stator 2 and a rotor 3, between which Flugelzellen or pressure chambers 4 are formed.
  • These pressure chambers 4 can not be seen in FIG. 1.
  • one of the pressure chambers 4 can be seen in FIGS. 2 and 3.
  • each pressure chamber is attached in a rotationally fixed manner to a rotor 5 by a vane 5.
  • working chambers 6 are formed.
  • One working chamber 6 is referred to as a late working chamber A and the other as an early working chamber B.
  • the Aroeits- cam 6 may also be referred to as work space.
  • a central valve 7 is screwed into the rotor 3 and the central valve 7 is actuated by a central magnet 8, namely a proportional magnet.
  • a hydraulic fluid supply device not shown, such as an oil pump, oil can then be spent in the working chambers 6 or oil removed from the working chambers 6 is also a receiving organ, such as a tank or ⁇ Kvanne. affiliated
  • an active accumulator ⁇ is also provided here.
  • the accumulator 9 is arranged below a camshaft rotation axis 10.
  • the camshaft rotation axis 10 can also be referred to briefly as the axis of rotation
  • the active accumulator ⁇ has a piston 1 1, which is biased by a spring 12.
  • the spring 12 biases the piston 1 1 in the direction of a storage space 13.
  • the reservoir 13 has em volume Vi on an actuator 14 is provided to unlock the active pressure accumulator 9 or lock.
  • the actuator 14 may be formed as a detent valve 15 It may also be formed as a solenoid valve 16 The actuator 14 causes when energized unlocking of the compression piston 1 serving 1
  • a camshaft 17 is provided to be rotatably connected to the rotor 3.
  • a valve 19 is provided to interrupt a ⁇ lzu- drive from the oil pump
  • a pressure medium line 20 is provided to connect an output 21 of the storage space 13 with the sliding bearing 18 and to allow oil access into the interior of the camshaft 17
  • the oil from the interior of the camshaft can then penetrate into the interior of the central valve 17 and reach the working chambers A or B through the inlets open if necessary.
  • the supply from the oil pump P is possible in particular from above (but also from another direction), ie on the O- side of the camshaft 17 on the sliding bearing or on the sliding bearing 18, while the supply from the active accumulator 9 is below at the sliding bearing 18.
  • vent 22 is provided to remove air from a spring chamber 23 - bz again suck in the spring chamber, when the piston prints oil from the memory 9
  • FIG. 2 the use of a 5/5-way valve 24 is shown.
  • the 5/5-way valve 24 has five inlets / outlets and five positions that it can take on the adjustment
  • the entrances / outlets lead to the hydraulic fluid supply device P, a tank T, the working chamber A. a Mitvemegelungs- gang 31 and the working chamber B.
  • the ittenverriegelungsposi- tion (MLP) is shown.
  • the processing chamber A has an extra opening region 27
  • FIG. 4 shows a flow / current diagram, in which the electric current I is plotted on the horizontal axis and the hydraulic medium flow Q is plotted on the vertical axis.
  • the hydraulic medium supply device P which is separate from the active pressure accumulator 9 Component is connected to the working chamber ß, whereas the working chamber A is connected to the tank.
  • the hydraulic medium supply device P is connected to the working chamber A and the working chamber B is connected to the tank
  • FIG. 7 shows the chronological sequence of the crankshaft speed (top part of the diagram), the scanning characteristic / pulse width modulation state, PWM for short, in the middle part and the angular position of the nucleation waveshutter (phaser position) in the lower region.
  • the crankshaft speed is indicated by the line 35.
  • the scanning confidence is indicated by the line 36.
  • the lock state is indicated by the line 37.
  • Ignition takes place only at time 44. This is the time of the so-called "first ignition ", ie first ignition.
  • FIG. 8 shows another state, namely a state in which less than approximately eight hours have elapsed between times 39 and 41, at least as much time that the engine or the internal combustion engine has not yet cooled down, at least not has cooled below 100 X or 80 X. This is the state of normal start stop action.
  • an active pressure accumulator 9 is formed via the pressure medium dispenser 20 (PP) with the central locking slide 31 in a locking cover 45.
  • the Mrttenverriegelungskulisse 31 is on the other side of a «sealing cover 46. seen from the rotor 3.
  • the Vernegelungapins 29 and 30 are inserted into the rotor 3 biased by springs 47 and 48
  • the wing 5 is »n its early position. so that the working chamber A is designed to be maximally large.
  • Em switching valve 49 is connected to the hydraulic supply unit P (Port C). However, the switching valve 49 is in such a position that an inflow of P to the active pressure accumulator 9 and also to the pressure medium line 20 is interrupted.
  • a control unit 50 is used
  • the rotor 3 is in an early position before engine start.
  • the rotor is already in a middle position where oil pressure on the pressure medium line 20 in the backdrop 31 by the active pressure accumulator 9 is available.
  • the rotor 3 is shown in FIG. 13 in its early position before the engine is started.
  • the rotor is again arranged between the locking cover 45 and the sealing cover 46.
  • the active accumulator ⁇ is not yet connected via the pressure medium line 20 (PP). It is therefore still “off ".
  • the rotor 3 is between its early position and However, the first pin 29 is already retracted into the Verlegelung 30th He intervenes there locking a
  • the active pressure accumulator 9 is still off, but is not, also as shown in Figure 13, the switching valve 49 to the port C, ie the pump P connected in Figure 15, the temporally subsequent state is shown, in which now also the second locking pin 30 enters the Vernegelungskulisse 31.
  • the second locking pin 30 is now also lockingly retracted into the slot 31, so that now the rotor 3 is locked in its center position by the locking pins 28.
  • the switching valve 49 may also be switched through, if instead of a 5/5-way valve in the position 1, the already disclosed variant of the 4 / 3- and 3/2-way valve use is desired.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

L'invention concerne un déphaseur hydraulique d'arbre à cames (1), du type à palettes, pourvu d'un stator (2) et d'un rotor (3) monté de manière à pouvoir tourner dans ce dernier lors d'un fonctionnement normal, le rotor (3) et le stator (2) formant au moins deux chambres de travail (6) disposées entre ces derniers, séparées par une palette (5) fixée au rotor, et pouvant être remplies de fluide hydraulique par un dispositif d'alimentation en fluide hydraulique. Dans l'état de verrouillage, au moins une broche de verrouillage (28) immobilise le rotor (3) pour qu'il soit bloqué en rotation par rapport au stator (2). La broche de verrouillage (28) est reliée à un accumulateur de pression (9) actif qui le déplace en cas en cas de besoin, la broche de verrouillage (28) et l'accumulateur de pression actif (9) coopérant de telle manière que la broche de verrouillage (28) empêche le blocage en rotation du rotor (3) par rapport au stator (2). L'invention concerne également un procédé permettant de verrouiller un rotor (3) d'un déphaseur hydraulique d'arbre à cames (1) par rapport à un stator (2) du déphaseur d'arbre à cames (1), selon lequel le rotor (3) peut être verrouillé par rapport au stator (2) dans une position centrale ainsi que dans une position avancée et/ou retardée, au moyen d'au moins une broche de verrouillage (28), et le fluide hydraulique d'un accumulateur de pression actif (9), séparé d'un dispositif d'alimentation en fluide hydraulique destiné au remplissage de chambres de travail (6) présent entre le rotor (3) et le stator (2), étant utilisé pour agir sur un mouvement longitudinal de la broche de verrouillage (28).
PCT/DE2014/200321 2013-09-23 2014-07-15 Verrouillage multiple d'un déphaseur d'arbre à cames et procédé pour faire fonctionner un déphaseur d'arbre à cames WO2015039653A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013219078.6 2013-09-23
DE102013219078.6A DE102013219078B4 (de) 2013-09-23 2013-09-23 Multiverriegelung eines Nockenwellenverstellers

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Publication Number Publication Date
WO2015039653A1 true WO2015039653A1 (fr) 2015-03-26

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PCT/DE2014/200321 WO2015039653A1 (fr) 2013-09-23 2014-07-15 Verrouillage multiple d'un déphaseur d'arbre à cames et procédé pour faire fonctionner un déphaseur d'arbre à cames

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DE (1) DE102013219078B4 (fr)
WO (1) WO2015039653A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019166042A1 (fr) * 2018-02-27 2019-09-06 Schaeffler Technologies AG & Co. KG Déphaseur d'arbres à cames hydraulique

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017126172B3 (de) 2017-11-09 2019-03-28 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller
DE102019113638B3 (de) * 2019-05-22 2020-09-17 Schaeffler Technologies AG & Co. KG Steuerventil mit einem integriertem aktiven Druckspeicher

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JPH09264110A (ja) * 1996-03-28 1997-10-07 Aisin Seiki Co Ltd 弁開閉時期制御装置
US6035819A (en) * 1998-01-30 2000-03-14 Aisin Seiki Kabushiki Kaisha Variable valve timing controller
DE102004048070A1 (de) 2004-10-02 2006-06-22 Schaeffler Kg Verfahren zum Betreiben einer hydraulisch betätigten Vorrichtung und Vorrichtung
EP2492459A2 (fr) * 2011-02-22 2012-08-29 Schwäbische Hüttenwerke Automotive GmbH Régulateur de phase d'arbres doté d'un dispositif de verrouillage amélioré
WO2012171670A1 (fr) 2011-06-16 2012-12-20 Schaeffler Technologies AG & Co. KG Régulateur d'arbre à cames

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Publication number Priority date Publication date Assignee Title
DE102008005277A1 (de) * 2008-01-19 2009-07-23 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
US9303536B2 (en) * 2011-11-04 2016-04-05 Aisin Seiki Kabushiki Kaisha Valve opening and closing control apparatus

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09264110A (ja) * 1996-03-28 1997-10-07 Aisin Seiki Co Ltd 弁開閉時期制御装置
US6035819A (en) * 1998-01-30 2000-03-14 Aisin Seiki Kabushiki Kaisha Variable valve timing controller
DE102004048070A1 (de) 2004-10-02 2006-06-22 Schaeffler Kg Verfahren zum Betreiben einer hydraulisch betätigten Vorrichtung und Vorrichtung
EP2492459A2 (fr) * 2011-02-22 2012-08-29 Schwäbische Hüttenwerke Automotive GmbH Régulateur de phase d'arbres doté d'un dispositif de verrouillage amélioré
WO2012171670A1 (fr) 2011-06-16 2012-12-20 Schaeffler Technologies AG & Co. KG Régulateur d'arbre à cames

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019166042A1 (fr) * 2018-02-27 2019-09-06 Schaeffler Technologies AG & Co. KG Déphaseur d'arbres à cames hydraulique
US11053820B2 (en) 2018-02-27 2021-07-06 Schaeffler Technologies AG & Co. KG Hydraulic camshaft adjuster

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DE102013219078A1 (de) 2015-03-26
DE102013219078B4 (de) 2021-02-18

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