EP3994369A1 - Antriebseinheit mit kühlmittelleitsystem zur zuführung und aufteilung eines fluidstroms zwischen zwei getriebeeingangswellen - Google Patents
Antriebseinheit mit kühlmittelleitsystem zur zuführung und aufteilung eines fluidstroms zwischen zwei getriebeeingangswellenInfo
- Publication number
- EP3994369A1 EP3994369A1 EP20740201.7A EP20740201A EP3994369A1 EP 3994369 A1 EP3994369 A1 EP 3994369A1 EP 20740201 A EP20740201 A EP 20740201A EP 3994369 A1 EP3994369 A1 EP 3994369A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- transmission input
- input shaft
- drive unit
- partial
- axially
- 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.)
- Withdrawn
Links
- 239000002826 coolant Substances 0.000 title claims abstract description 17
- 239000012530 fluid Substances 0.000 title claims abstract description 10
- 238000005096 rolling process Methods 0.000 claims abstract 4
- 230000005540 biological transmission Effects 0.000 claims description 83
- 238000004519 manufacturing process Methods 0.000 description 5
- 238000001816 cooling Methods 0.000 description 4
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 108010001267 Protein Subunits Proteins 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Classifications
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
- F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
- F16C33/6674—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to the amount supplied, e.g. gaps to restrict flow of the liquid
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/44—Needle bearings
- F16C19/46—Needle bearings with one row or needles
- F16C19/463—Needle bearings with one row or needles consisting of needle rollers held in a cage, i.e. subunit without race rings
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/02—Flow, e.g. volume flow or mass flow
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0661—Hydraulically actuated multiple lamellae clutches
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2300/00—Special features for couplings or clutches
- F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84
Definitions
- the invention relates to a drive unit for a motor vehicle drive train, d. H. a drive train of a motor vehicle, such as a car, truck, bus or other commercial vehicle, with a double clutch, two coaxially arranged transmission input shafts rotatably mounted relative to each other via a roller bearing, a first partial clutch of the double clutch being operatively connected to a first transmission input shaft and a second partial clutch of the double clutch is operatively connected to a second transmission input shaft arranged radially outside the first transmission input shaft, as well as to a coolant control system which is partially implemented by a radial gap between the two transmission input shafts, the coolant control system being designed such that a first partial flow, which leads axially to the roller bearing, and a second partial flow, which axially opposes the first partial flow and is larger than the first partial flow, are generated.
- Prior art of the generic type is known from CN 104061319 B, for example.
- the division of different partial flows takes place through two axially spaced through bores in the second transmission input shaft and through a separate seal between the transmission input shafts.
- a disadvantage of the designs known from this prior art is, however, that an additional / relatively high drag torque acts on the driven transmission input shaft between the two transmission input shafts for dividing the partial flows.
- the manufacture and assembly of one of the two transmission input shafts are relatively complex.
- the two transmission input shafts are axially spaced apart radially from one another, extending from the roller bearing to a free axial end of the second transmission input shaft.
- the radial gap formed between the Wälzla ger and the free end of the second transmission input shaft is thus implemented axially continuously. The existing drag torque is thereby further reduced.
- a first section of the radial gap located axially between the inlet opening and the roller bearing has a smaller (minima len) flow cross-section than a second sub-section of the radial gap located axially between the inlet opening and the free axial end of the second transmission input shaft. This cleverly divides the two partial flows. It is also advantageous if at least one radial shoulder that narrows the first partial section is formed on the first transmission input shaft and / or on the second transmission input shaft. This radial shoulder is particularly preferably implemented on the radial outside of the first transmission input shaft. This further reduces the manufacturing effort.
- a first radial shoulder is formed / arranged towards an (axial) end of the first partial section facing the inlet opening.
- This first radial shoulder is further preferably implemented (with the implementation of a gap seal) directly by a radial shoulder.
- a second radial shoulder (in addition to or as an alternative to the first radial shoulder) is formed / arranged at an (axial) end of the first section facing the roller bearing.
- the second radial shoulder is also preferably implemented as a radial shoulder.
- a slave cylinder of a hydraulic actuating device which interacts with at least one of the partial clutches is supported radially from the outside on the second transmission input shaft. This makes the drive unit particularly compact.
- a cylinder housing of the slave cylinder forms a supply channel of the coolant control system leading to the inlet opening, the coolant control system is still particularly cleverly integrated into the already existing components of the drive unit.
- a first seal is preferably arranged to a first axial side of the inlet opening, while a second seal to one of the first axial side facing away from the second axial side of the inlet opening is arranged towards.
- a supply and distribution of a cooling oil between the transmission input shafts is realized. It is proposed to make the distribution of the cooling oil volume storm in the gap between the transmission input shafts. This eliminates the previous division across different total cross-sectional areas of different bores.
- Fig. 1 is a longitudinal sectional view of a drive unit according to the invention according to a first embodiment, in which the entire structure of the drive unit can be clearly seen,
- FIG. 2 shows a detailed longitudinal sectional view of the drive unit of FIG. 1 in an area of a radiator gap designed to split a fluid flow between two existing transmission input shafts
- Fig. 3 is a detailed longitudinal sectional view of a drive unit according to the invention according to a second embodiment in the area as it was already selected in Fig. 2, wherein the radial gap is implemented in a slightly different way compared to the first embodiment.
- a drive unit 1 according to the invention is shown according to a preferred first embodiment.
- the drive unit 1 is typically in one Drive train of a motor vehicle and thus used in operation in the direction of torque transmission between an internal combustion engine and a transmission.
- the drive unit 1 is provided with a double clutch 2.
- the double clutch 2 is inserted between an input / input shaft 23 of the drive unit 1 and two transmission input shafts 4, 5.
- a first partial clutch 6a of the double clutch 2 is used between the input shaft 23 and a first transmission input shaft 4 of a transmission, not shown here for the sake of clarity, and a second partial clutch 6b of the double clutch 2 is effective between the input shaft 23 and a second transmission input shaft 5 used.
- the transmission input shafts 4, 5 are arranged coaxially to one another and consequently have a common axis of rotation 26 about which they can be driven.
- the directions used axially, radially and in the circumferential direction relate to this axis of rotation 26, so that with axial a direction along / parallel to the axis of rotation 26, with radial a direction normal to the axis of rotation 26 and with the circumferential direction a direction tangential to one about the axis of rotation 26 coaxial circular line is meant ge.
- the respective partial clutch 6a, 6b is implemented as a friction disk clutch and is actuated via a hydraulic actuating device 19.
- the hydraulic actuator 19 has a slave cylinder 18.
- This slave cylinder 18 is implemented as a concentric slave cylinder 18.
- the slave cylinder 18 has two sub-units, each sub-unit having an actuating effect on one of the two sub-clutches 6a, 6b via its corresponding piston.
- the respective partial clutch 6a, 6b has a friction disk set 24a, 24b due to its design as a friction disk clutch.
- the first partial clutch 6a is arranged with its (first) friction plate set 24a radially outside of a (second) friction plate set 24b of the second partial clutch 6b.
- a coolant control system 8 is provided to cool different constituent parts of the drive unit 1, in particular the friction disk packs 24a, 24b and a (first) roller bearing 3 inserted between the two transmission input shafts 4, 5.
- the coolant control system 8 is partially formed in a cylinder housing 20 of the slave cylinder 18. In Fig. 1, a part of a feed channel 21 can be seen radially between the cylinder housing 20 and the second transmission input shaft 5.
- This zuleitkanal 21 opens on its radial inside directly into an inlet opening 10 of the coolant control system 8.
- the inlet opening 10 is implemented here by a radial through hole in the second transmission input shaft 5 designed as a hollow shaft.
- there are typically a plurality of inlet openings 10 which are distributed in the circumferential direction and which are connected to the feed channel 21 which is set as an annular gap.
- the supply channel 21 is sealed on a first axial side of the inlet opening 10 with a first seal 22a and on a second axial side of the inlet opening 10 opposite the first axial side with a second seal 22b, which seals 22a, 22b between the cylinder housing 20 and the second transmission input shaft 5 are arranged.
- a radial gap 7 of the coolant control system 8 directly adjoins the inlet opening 10 radially inside the inlet opening 10.
- the radial gap 7 is that gap which is located radially between the first transmission input shaft 4 formed as a solid shaft and the second transmission input shaft 5 arranged radially outside the first transmission input shaft 4 and designed as a hollow shaft.
- the two transmission input shafts 4, 5 are, as already mentioned, arranged coaxially to one another, the second transmission input shaft 5 with its hollow section being pushed onto the first transmission input shaft 4 from the outside.
- the first roller bearing 3, which here is a needle bearing, is used to support the two transmission input shafts 4, 5 relative to one another.
- the first transmission input shaft 4 also accommodates a further second roller bearing 25.
- the second roller bearing 25, which serves to support the input shaft 23 relative to the first transmission input shaft 4, is arranged on the first transmission shaft 4 on an axial side facing the input shaft 23.
- the second roller bearing 25 is also implemented here as a needle bearing.
- the radial gap 7, as again shown in Fig. 2, is divided into two sections 13, 14 un. The two subsections 13, 14 run from the inlet opening 10 in mutually opposite axial directions. Accordingly, a first section 13 of the radial gap 7 is implemented axially between the inlet opening 10 and the first Wälzla ger 3.
- a second section 14, which connects to the first section 13, is implemented axially between the input opening 10 and a (free) end 12 of the second transmission input shaft 5.
- the second section 14 extends beyond the free end 12 and occurs from there radially outward in corresponding areas of the partial couplings 6a, 6b.
- the free end 12 typically protrudes axially so far towards the friction plate packs 24a, 24b that, during operation, the centrifugal force effect that occurs, the fluid conveyed through the second section 14 of the radial gap 7 automatically radially outwards from the second section 14 becomes.
- the two transmission input shafts 4, 5 and the roller bearing 3 are designed and coordinated with one another in such a way that a division of a fluid flow 11, which flows radially inwardly through the input opening 10 of the second transmission input shaft 5 during operation, into the first and second partial flows 9a, 9b directly within of the radial gap 7 takes place.
- the two subsections 13, 14 are specifically implemented with different flow cross-sections. A (minimal) first flow cross section of the first subsection 13 is smaller than a (minimal) second flow cross section of the second subsection 14.
- the first transmission input shaft 4 has, on its radial outer side, a first set 15 which forms a radial shoulder.
- This first shoulder 15 tapers the radial gap 7 / the cross section of the radial gap 7 in such a way that a type of gap seal is formed radially between the transmission input shafts 4, 5.
- the first shoulder 15 is arranged at a first axial end 17 a of the first partial section 13 facing the inlet opening 10.
- a further second shoulder 16 is present at a second axial end 17b of the first partial section 13 which is axially opposite the first end 17a.
- This second paragraph 16 is also called radial Shoulder realized and tapered in turn the radial gap 7 / the cross section of the Ra dialspalts 7.
- the second paragraph 16 directly forms an axial stop surface for the first roller bearing 3.
- the setting of the flow cross section and the division of the partial flows 9a, 9b can also take place in a different manner.
- the first paragraph 15 can also be designed to be smaller than the second paragraph 16 or even be omitted in other embodiments.
- the first roller bearing 3 can be held as a flow barrier and even both paragraphs 15, 16 can be omitted.
- one idea of the invention is that the distribution of the cooling oil volume flow to supply the clutch (second partial flow 9b) and to supply the bearings 3 (first partial flow 9a) between the transmission input shafts 4, 5 in the gap 7 between the second transmission input shaft 5 and the first Ge transmission input shaft 4 takes place. This eliminates the previous division over different total cross-sectional areas of the bores in the second transmission input shaft 5.
- a current division has been made as follows: Supply to clutch 2 (via second partial flow 9b): 6 x 06 mm; Supply of bearings 3 (via the first part of current 9a): 1 x 02.5; ie the flow resistance differs approximately by the factor 200 and thus approx. 0.075 l / min arrive at bearing 3 from 15 l / min total volume flow 11.
- the distribution of the volume flow 11 for the bearing 3 (via the first part of the current 9a) can be done via: 1.
- the gap should roughly be approx. 5 mm long (axial extension) and an outer diameter of 25, 5 mm and an inside diameter of 25.06 mm, so that approx. 0.075 l / min flow to bearing 3.
- the total cooling oil volume flow is directed to the second transmission input shaft 5 via the CSC housing 20 and sealed to the second transmission input shaft 5 by means of two seals 22a, 22b.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102019118079.1A DE102019118079B4 (de) | 2019-07-04 | 2019-07-04 | Antriebseinheit mit Kühlmittelleitsystem zur Zuführung und Aufteilung eines Fluidstroms zwischen zwei Getriebeeingangswellen |
PCT/DE2020/100465 WO2021000988A1 (de) | 2019-07-04 | 2020-06-04 | Antriebseinheit mit kühlmittelleitsystem zur zuführung und aufteilung eines fluidstroms zwischen zwei getriebeeingangswellen |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3994369A1 true EP3994369A1 (de) | 2022-05-11 |
Family
ID=71614635
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20740201.7A Withdrawn EP3994369A1 (de) | 2019-07-04 | 2020-06-04 | Antriebseinheit mit kühlmittelleitsystem zur zuführung und aufteilung eines fluidstroms zwischen zwei getriebeeingangswellen |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP3994369A1 (de) |
KR (1) | KR20220029583A (de) |
CN (1) | CN113939667A (de) |
DE (1) | DE102019118079B4 (de) |
WO (1) | WO2021000988A1 (de) |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10004189C5 (de) * | 1999-09-30 | 2015-05-21 | Volkswagen Ag | Mehrfach-Kupplungseinrichtung |
DE10114281B4 (de) * | 2001-03-23 | 2008-12-11 | Zf Sachs Ag | Mehrfach-Kupplungseinrichtung und Radiallagerungskonzept hierfür |
DE102004012948B4 (de) * | 2004-03-17 | 2012-05-31 | Zf Friedrichshafen Ag | Doppelkupplungseinrichtung in axialer Bauart |
DE102005045158A1 (de) * | 2005-09-21 | 2007-03-22 | Zf Friedrichshafen Ag | Doppel-Kupplungseinrichtung und Axial-Abstützungseinrichtung hierfür |
US7784595B2 (en) * | 2006-02-13 | 2010-08-31 | Borgwarner Inc. | Integrated clutch assembly damper arrangement |
CN104061319B (zh) * | 2014-03-05 | 2016-08-17 | 宁波吉利罗佑发动机零部件有限公司 | 一种用于双离合器变速器的双离合器润滑结构 |
-
2019
- 2019-07-04 DE DE102019118079.1A patent/DE102019118079B4/de active Active
-
2020
- 2020-06-04 CN CN202080042660.XA patent/CN113939667A/zh active Pending
- 2020-06-04 KR KR1020217042376A patent/KR20220029583A/ko unknown
- 2020-06-04 EP EP20740201.7A patent/EP3994369A1/de not_active Withdrawn
- 2020-06-04 WO PCT/DE2020/100465 patent/WO2021000988A1/de unknown
Also Published As
Publication number | Publication date |
---|---|
WO2021000988A1 (de) | 2021-01-07 |
KR20220029583A (ko) | 2022-03-08 |
CN113939667A (zh) | 2022-01-14 |
DE102019118079A1 (de) | 2021-01-07 |
DE102019118079B4 (de) | 2021-03-18 |
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