EP3658781A1 - Durchströmbare anordnung - Google Patents
Durchströmbare anordnungInfo
- Publication number
- EP3658781A1 EP3658781A1 EP18759898.2A EP18759898A EP3658781A1 EP 3658781 A1 EP3658781 A1 EP 3658781A1 EP 18759898 A EP18759898 A EP 18759898A EP 3658781 A1 EP3658781 A1 EP 3658781A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- diffuser
- impeller
- dff
- axial
- vne
- 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
Links
- 239000012530 fluid Substances 0.000 claims abstract description 12
- 238000000034 method Methods 0.000 claims abstract description 11
- 230000002093 peripheral effect Effects 0.000 claims description 2
- 238000011144 upstream manufacturing Methods 0.000 claims description 2
- 238000011161 development Methods 0.000 description 9
- 230000018109 developmental process Effects 0.000 description 9
- 230000000694 effects Effects 0.000 description 3
- 235000010678 Paulownia tomentosa Nutrition 0.000 description 2
- 240000002834 Paulownia tomentosa Species 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 210000003608 fece Anatomy 0.000 description 2
- 241001136792 Alle Species 0.000 description 1
- 239000000853 adhesive Substances 0.000 description 1
- 230000001070 adhesive effect Effects 0.000 description 1
- 238000009792 diffusion process Methods 0.000 description 1
- 230000014509 gene expression Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000001629 suppression Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
- F04D29/444—Bladed diffusers
Definitions
- the invention relates to an arrangement which zessfluid of a product along a main direction of flow can flow, comprising sor a standing about an axis in a direction of rotation rotatable impeller and a downstream impeller be ⁇ -sensitive bladed with vanes diffu-, said impeller an inlet for a wesentli ⁇ chen axial inflow and an outlet for a wesent ⁇ union radial outflow, wherein between a wheel disc and a cover plate of the impeller radially and axially extending blades are arranged, the rad- radkanäle in a circumferential direction delimit each other wherein the diffuser extends substantially radially along a main flow direction, the diffuser having an axial shroud side and an axial wheel disk side defining therebetween an axial channel width of the diffuser, the diffuser entering a diffuser for a substantially radial inflow and a diffuser outlet, wherein between the Radusionnseite and the cover ⁇ disk side
- EP 2 650 546 AI known.
- the guide vanes in inclined form in a standing behind the impeller stationary diffuser (dihedral vanes).
- the so-called “low solidity diffuser” (with guide vanes having a relatively large distance from one another in the circumferential direction in relation to their Radialerstre- suppression), to means of this aerodynamic measure a reduced pressure loss can be achieved. Since the Strö ⁇ mung image significantly in the diffuser, however, can depend on the flow conditions in and after the impeller the proposed measures, depending on the constellation of the impeller have positive or negative effects, so that the ge ⁇ wished effect of this measure only under certain other aerodynamic conditions or not will be matched one.
- Radial compressor impeller known whose cover plate and wheel ⁇ disc are formed on the outer circumference as conical surfaces.
- WO 2011/011335 A1 each show a three-dimensional diffuser vane design downstream of an open impeller.
- the flow conditions on an open impeller are not comparable with those in a closed impeller because of the adhesive condition even on Strömungstre- rende stator relative to the wheel disc on the open impeller. Downstream of an open impeller therefore results in completely different flow patterns, in particular with regard to the differences on the part of the wheel disc and the cover plate.
- EP 0,648,939 A2 shows a turbo machine with a ge ⁇ closed impeller.
- EP 2650546 Al shows a Leitschaufeltreatment with a curved profile centroid line along the blade height ⁇ downstream of a closed impeller. So far, a three-dimensional design of impeller ⁇ blades and Diffusorschaufein hardly follows a traceable technical teaching that improves the aerodynamics of the arrangement reliably over conventional designs. It is therefore an object of the invention to improve the aerodynamics, in particular the guide vanes of the diffuser of such an arrangement, by means of the teaching according to the invention.
- the invention proposes an arrangement of the type defined above, which is further formed by means of the characterizing part of the main claim.
- the individual vanes can be defined as a stack of blade profiles along a blade height.
- the blade profiles here are two-dimensional geometries that define the blade outer contour in a specific blade height position.
- the invention understands a ("imaginary") straight connecting line between the profile leading edge (profile nose) and a profile chord of a blade profile
- the angle of attack of a blade profile corresponds to the angle between the tangent to the chord and the tangent to the circular motion of the rotor. Accordingly, along the extension of the blade of the Anstellwin ⁇ angle is perpendicular to the blade height, that is substantially parallel to the main flow direction ⁇ constant and can be moved along the blade height variie ⁇ ren.
- a skeleton line describes a profile ⁇ section or a profile of a blade in a certain height position in that the skeleton line (curvature line) is a line inscribed by the center points or the suction side and pressure side of the profile tangent circles defined line.
- Expressions such as axial, radial, tangential or circumferential direction relate - unless otherwise indicated - to a rotational axis of the impeller of the assembly.
- the terms "tangential”, “tangent” and related terms are often used in the description of this invention with respect to another curve.
- a process fluid may in the present case be any gaseous, liquid or mixed-phase fluid.
- the process fluid be ⁇ moved along a main flow direction through the purchase order, which is part of a turbomachine generally.
- the outflow direction is understood to be the mean direction of travel of the process fluid in the region which is defined in the respective context of physical boundary walls.
- the process fluid passes through individual of Leit ⁇ shovel limited axial and limited circumferential flow channels from a region of the inlet edges of the guide vanes radially outward in a range of trailing edges of the vanes into it. Since the guide vanes each have a curvature of the profile, it is only possible to speak of a substantially radial main flow direction.
- the impeller of the assembly includes a wheel disc and a cover disc on a rule.
- the wheel disc hereby limited flow channels of the impeller on the one hand radially (vorwie ⁇ quietly in the area of inflow) inside and, on the other hand, to the axial side (increasingly close to the impeller outlet) axially opposite the inflow side and through which a process fluid does not flow into the impeller
- the cover disc represents the boundary of flow channels of the impeller opposite the wheel disc the Radusionnseite opposite axial shroud side flows the process fluid axially into the impeller and is deflected for the flow channels of the impeller radially outward.
- the cover plate side could therefore be called the inflow side.
- the blades connect the wheel disc and the cover plate together.
- the wheel disc and the cover disc also define the wheel disc side and the cover disc side, respectively, to which reference will also be made in the description of the diffuser.
- the inflow of the diffuser in the arrangement according to the invention always takes place radially from the inside to the outside.
- the diffuser is preferably also provided with a substantially radially outward direction
- the diffuser is also curved and optionally flows radially-axially, axially or radially inward flows.
- a section of the diffuser always extends substantially radially. This section can be located in front of a deflection of the flow in an axial or in a radially inward flow direction.
- a leading edge angle for each axial blade height is defined as Win ⁇ angle between a leading edge tangent to a skeleton ⁇ line to a leading edge of each vane and a circumferential tangent through the inlet edge, the
- Admission edge angle cover plate side is smaller than the wheel side.
- a circumferential tangent which extends through the inlet ridge occurs that this circumferential tangent perpendicular to a radial line through the leading edge point of the jewei ⁇ time profile section of the vane.
- the A ⁇ occurs edge angle here is the mathematically positive over- dashed angles from the circumferential tangent to the entrance edge tangent to the skeleton line.
- An advantageous development of the invention provides that the difference between the cover plate side and the wheel disc soapy entry edge angle is at least 5 °.
- An inventive embodiment of the invention in this order of magnitude leads to a significant improvement in the aerodynamic properties of the arrangement.
- Another advantageous development of the invention provides that the angle of attack of the guide vanes is smaller on the side of the cover disk than on the side of the wheel disk. This embodiment takes into account the difference in the flow pattern after exiting the impeller between the cover plate side and the wheel disc side in addition, so that the aerodynamics is further improved.
- Another development of the invention provides that the flow is prepared particularly expedient after exiting the impeller before entering the diffuser when the quotient of the axial channel width of the bladed diffuser to the maximum impeller outlet diameter is greater than 0.04.
- Another advantageous development of the invention provides that the ratio of the axial channel width of the diffuser contemplative feiten to the axial channel width of the impeller at the ma imum ⁇ rotor outlet diameter is smaller than 0.95. In this way, the flow with the entry into the diffusion accelerated, so that the vortex formation behind the Lauf ⁇ rad reduces.
- dung the guide vanes are formed such that a win ⁇ angle between a tangent to the skeleton line in the entry ⁇ edge portion to a tangent to the skeleton line in the off ⁇ takes edge portion of the cover disk each small disk-side and wheel.
- this feature can be characterized in that a deflecting function predetermined by the respective profile is less strong on the cover plate side than on the wheel disk side.
- This refinement also relates advantageously to the particular flow situation of the process fluid after it leaves the impeller and before it enters the diffuser.
- a similar effect has another advantageous Wide Erbil ⁇ dung of the inventive arrangement, in which the guide vanes are formed such that an angle between a tangent to the skeleton line in the leading edge region to the profile chord is cover plate side is smaller than wheel discs ⁇ other.
- the angle between a tangent to the skeleton line in the leading edge region to the profile chord is de ⁇ finiert than the mathematically positive angle of the tangent to the skeleton line in the leading edge region to the profile chord.
- the guide vanes have an inclination, such that the leading edge is offset on the cover disc side opposite the wheel-side leading edge opposite to the rotational direction of the impeller by at least 10% of the axial channel width of the diffuser.
- this embodiment takes into account the differences between the shroud side and the wheel ⁇ disk side in the flow image after exiting the impeller additionally.
- the trailing edge may also be inclined in the circumferential direction, and it is particularly expedient for an advantageous further development of the arrangement if the trailing edge is in the circumferential direction
- Guide vanes are designed such that an offset ent ⁇ against the rotational direction of the impeller at the trailing edge of the cover plate side opposite the Radterionsei ⁇ te is lower than at the leading edge.
- a harmonious, low-pressure flow control is achieved in particular when the axial course (course in the vertical direction) of the vanes of the diffuser from the cover plate side to the Radepticnseite is continuously ge ⁇ curved executed.
- FIG. 1 shows a schematic longitudinal section through an arrangement according to the invention
- FIG. 3 shows a schematic cross section through an arrangement according to the invention
- FIG. 5 shows a schematic cross section through a diffuser of an arrangement according to the invention in the region of a single guide blade.
- Figures 1 and 2 show a schematic representation
- An inventive arrangement ARG is flowed through by a process fluid PFF along a main flow direction MFD from an inlet INL to an outlet EXT.
- ARG comprises a rotatable about an axis X in Rotationsrich- tung RTD impeller IMP.
- the IMP Downstream of the Laufra ⁇ the IMP is a bladed with vanes VNE stationary diffuser DFF.
- the impeller IMP has an inlet INI for a substantially axial inflow and a outlet EXI for substantially radial outflow.
- the suitability for the substantially axial inflow or the outflow of the substantially radial impeller is characterized by the course of itself through the impeller IMP réellere ⁇ -bridging the flow duct and the impeller channels ICH.
- Zvi ⁇ rule HWI a wheel disc and a cover disc of the impeller SWI IMP are located radially and axially extending blades BLD.
- the blade channels ICH are separated from each other by these blades in BLD in a circumferential direction CDR, as can be seen in FIGS. 3 and 4.
- the diffuser DFF extends with
- the diffuser DFF has an axial cover plate side SWS and an axi ⁇ alle wheel disc side HWS. This nomenclature is based on the arrangement of the cover disc SWI and the wheel disc HWI of the impeller IMP.
- the axial shroud side SWS and the axial Radusionnseite HWS of the diffuser DFF limit Zvi ⁇ to rule an axial channel width of the diffuser IAC DFF.
- the diffuser has a diffuser inlet DFF IND for the radial inflow We ⁇ sentlichen and a diffuser outlet EXD on.
- the diffuser is subdivided into three sections extending along the main flow direction MFD, into a first diffuser third TS1, a second one
- Zvi ⁇ rule Radularnseite the cervical spine and the cover plate side SWS extend axially along a blade height direction and radially extending along a flow direction Vanes VNE.
- the vanes VNE delimit individual vane channels HCN from each other in a circumferential direction CDR.
- Figures 3, 4 and 5 a cross section of he ⁇ inventive arrangement ARG or a section is respectively reproduced therefrom, so that it is also apparent how the Leitschaufelkanäle HCN tung each other in a the circumferential CDR are delimited by means of the guide vanes VNE. Since the vanes VNE by nature not a completely straight
- the individual vanes VNE can be described as a stack of blade profiles PRL (for example, blade profile
- the blade profiles PRL themselves are two-dimensional geometries that define the blade outer contour in a specific blade elevation position. The actual three-dimensional
- the outer contour of the blade on the respective suction side SCS and pressure side PRS results as a surface interpolation between the linear boundary contours of the blade profiles PRL, which each indicate a linear specification in the respective blade height position (here also axial position).
- FIG 3 shows in cross-section schematic fragmentary the arrangement according to the invention with an impeller ARG IMP and ei ⁇ nem downstream diffuser subsequent DFF, which is designed as a stator STA.
- IMP between the impeller and the diffuser DFF is a radial clearance RCL a Radi ⁇ alspaltes.
- the impeller IMP rotates in the illustration in a circumferential direction CDR.
- the individual guide vanes VNE of the diffuser DFF are merely reproduced as schematic skeleton lines BWL.
- a skeleton line BWL here describes a profile section or a profile of a blade in a certain height position in that the skeleton line BWL, also sometimes called curvature line, one of the Mit- is the center of a defined line or the suction side and the pressure side of the profile tangent circles.
- FIG. 5 uses two circles CLC to show, by way of example, how pressure side PRF and suction side SCS of a vane VNE define the skeleton line BWL by means of the inscribed circles CLC.
- Figure 5 shows only an axial section through the diffuser DFF in the region of a vane VNS, the figure has validity for both the cover plate side SWS, as well as for the wheel disc side HWS.
- FIG. 4 shows similar relationships in conjunction with the impeller IMP.
- the impeller IMP is divided into three along the main flow direction MFD successive Drittab ⁇ sections in approximately starting from a blade inlet edge ILE up to a blade outlet edge ITE.
- the blade inlet edge ILE and the blade outlet edge ITE are not necessarily identical to the inlet INI of the impeller or outlet XEI of the impeller.
- the main flow direction MFD also runs axially in the impeller IMP - ie also in the drawing plane in FIG. 4.
- the in ⁇ formation over the axial goes naturally verlo- ren in the axial projection of the rotor blades BLD of Figure 4.
- the impeller has a first impeller portion IS1, egg ⁇ NEN second impeller portion IS2 and a third Laufradab ⁇ section IS3 on.
- the fi gure 4 in each dashed reproduction shows the cover disk side SWS and the wheel disk side HWS both for a running shoe BLD and for a guide blade VNE.
- an ingress edge angle ⁇ LEA is defined for each axial blade as the angle between a leading edge tangent TLV of jewei- time vane VNE and a circumferential tangent CTG by the leading edge DLE.
- the entry edge angle LEA is mathematically positively measured from the circumferential tangent CTG on the entrance edge tangent TLV.
- the Peripheral tangent CTG is a tangent to the circumferential direction in the respective indicated position, here at the position of the leading edge DLE.
- This circumferential tangent CTG can also be defined as being perpendicular to a radial ray RAD and the reference point, here including the leading edge DLE.
- the profile chord VCH of the profile of the vane VNE is also drawn into the respective section, which extends from an entry edge DLE to a exit edge DTE as a straight line.
- the pitch angle AOA is also defined as a mathematically positive measured angle from the circumferential tangent CTG to the chord VCH.
- the arrangement ARG provides that the entry edge angle LEA cover plate side is smaller than the wheel disk side in the diffuser DFF.
- the difference between the cover-disk-side and the wheel-disk-side entry edge angle LEA is preferably at least 5 degrees.
- the quotient of the axial channel width SAC of the bladed diffuser DFF to the maximum impeller outlet diameter is more than 0.04. It can also be deduced from FIG. 2 that the quotient of an axial channel width SAC of the bladed diffuser DFF to the axial channel width IAC of the impeller IMP at the maximum impeller outlet diameter DIE is less than 0.95.
- the routing ⁇ shovel VNE is formed such that an angle, here ge ⁇ Nannt profile camber angle VBA, between a tangent TLV to the skeleton line BWL in the leading edge region to a tangent TTV on the skeleton line BWL in Austrittskantenbe ⁇ rich TEA cover plate side is smaller than Radusionnsei ⁇ tig.
- the angle of curvature VBA is here again mathematical measured positive from the tangent TLV on the skeleton line BWL in the entry edge area.
- FIG. 5 fundamentally reproduces the relationships on the wheel disk side HWS or cover disk side SWS and accordingly represents both sides.
- a leading edge of the vanes DLE VNE can ⁇ advantageous way, as shown in Figure 4, a piece of downstream passageway radially Windone be offset from the diffuser inlet DFF, wherein in figure 4, this radial offset is designated as CBS.
- FIG. 4 Schematically represented in FIG. 4 is the relationship that the guide vanes VNE have a tendency such that the entry edge DLE covers the disk side opposite the wheel-disk-side leading edge DLE against the rotational direction RTD of the impeller IMP by at least 10% of the axial channel width SAC of the diffuser DFF is offset.
- the vanes VNE are formed such that an offset against the rotational direction RTD of the impeller IMP at the trailing edge DTE of the cover plate side SWS against the Radusionnseite HWS is lower than at the leading edge DLE.
- the axial course of the guide view of the diffuser DFF from the cover disk side SWS to the wheel disk side HWS is continuously curved.
- FIG. 4 also shows schematically that at least in the most upstream third of the extension of the guide vanes VNE along the main flow direction MFD, an axial projection of a cover-side guide blade track DDS and a wheel-side guide rail DRS at least one projection of cover-side guide track DDS to the wheel-side guide track DRS of at least an area ratio> 5% the cover plate side vane track surface has.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP17192109.1A EP3460256A1 (de) | 2017-09-20 | 2017-09-20 | Durchströmbare anordnung |
PCT/EP2018/072379 WO2019057413A1 (de) | 2017-09-20 | 2018-08-20 | Durchströmbare anordnung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3658781A1 true EP3658781A1 (de) | 2020-06-03 |
EP3658781B1 EP3658781B1 (de) | 2023-01-11 |
Family
ID=59923318
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17192109.1A Withdrawn EP3460256A1 (de) | 2017-09-20 | 2017-09-20 | Durchströmbare anordnung |
EP18759898.2A Active EP3658781B1 (de) | 2017-09-20 | 2018-08-20 | Durchströmbare anordnung |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17192109.1A Withdrawn EP3460256A1 (de) | 2017-09-20 | 2017-09-20 | Durchströmbare anordnung |
Country Status (5)
Country | Link |
---|---|
US (1) | US11225977B2 (de) |
EP (2) | EP3460256A1 (de) |
JP (1) | JP7074957B2 (de) |
CN (1) | CN111133203B (de) |
WO (1) | WO2019057413A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3760871A1 (de) | 2019-07-04 | 2021-01-06 | Siemens Aktiengesellschaft | Diffusor für eine strömungsmaschine |
EP3760876A1 (de) | 2019-07-04 | 2021-01-06 | Siemens Aktiengesellschaft | Diffusor für eine strömungsmaschine |
EP3805572A1 (de) | 2019-10-07 | 2021-04-14 | Siemens Aktiengesellschaft | Diffusor, radialturboverdichter |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2372880A (en) * | 1944-01-11 | 1945-04-03 | Wright Aeronautical Corp | Centrifugal compressor diffuser vanes |
US3460748A (en) * | 1967-11-01 | 1969-08-12 | Gen Electric | Radial flow machine |
JPS5469811A (en) * | 1977-11-14 | 1979-06-05 | Hitachi Ltd | Diffuser for centrifugal compressor |
CN2045433U (zh) * | 1988-09-26 | 1989-10-04 | 上海机械学院 | 混流式风机 |
JP3482668B2 (ja) * | 1993-10-18 | 2003-12-22 | 株式会社日立製作所 | 遠心形流体機械 |
DE69526840T2 (de) | 1994-12-28 | 2003-01-23 | Ebara Corp | Turbomaschine mit Strömungsleiteinrichtungen mit variablem Winkel |
US8016557B2 (en) * | 2005-08-09 | 2011-09-13 | Praxair Technology, Inc. | Airfoil diffuser for a centrifugal compressor |
US9222485B2 (en) * | 2009-07-19 | 2015-12-29 | Paul C. Brown | Centrifugal compressor diffuser |
DE102010020379A1 (de) | 2010-05-12 | 2011-11-17 | Siemens Aktiengesellschaft | Einstellbarer Radialverdichterdiffusor |
US8616836B2 (en) * | 2010-07-19 | 2013-12-31 | Cameron International Corporation | Diffuser using detachable vanes |
JP5608062B2 (ja) | 2010-12-10 | 2014-10-15 | 株式会社日立製作所 | 遠心型ターボ機械 |
US9581170B2 (en) * | 2013-03-15 | 2017-02-28 | Honeywell International Inc. | Methods of designing and making diffuser vanes in a centrifugal compressor |
WO2015019901A1 (ja) * | 2013-08-06 | 2015-02-12 | 株式会社Ihi | 遠心圧縮機及び過給機 |
DE102013114609A1 (de) | 2013-12-20 | 2015-06-25 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Radial-Laufrad für einen Trommellüfter und Lüftereinheit mit einem derartigen Radial-Laufrad |
JP6242775B2 (ja) * | 2014-09-18 | 2017-12-06 | 三菱重工業株式会社 | 遠心圧縮機 |
DE102014219107A1 (de) | 2014-09-23 | 2016-03-24 | Siemens Aktiengesellschaft | Radialverdichterlaufrad und zugehöriger Radialverdichter |
DE102014222877A1 (de) | 2014-11-10 | 2016-05-12 | Siemens Aktiengesellschaft | Laufrad einer Radialturbofluidenergiemaschine, Stufe |
DE102016201256A1 (de) | 2016-01-28 | 2017-08-03 | Siemens Aktiengesellschaft | Strömungsmaschine mit beschaufeltem Diffusor |
GB2555567A (en) * | 2016-09-21 | 2018-05-09 | Cummins Ltd | Turbine wheel for a turbo-machine |
-
2017
- 2017-09-20 EP EP17192109.1A patent/EP3460256A1/de not_active Withdrawn
-
2018
- 2018-08-20 JP JP2020516698A patent/JP7074957B2/ja active Active
- 2018-08-20 EP EP18759898.2A patent/EP3658781B1/de active Active
- 2018-08-20 CN CN201880060914.3A patent/CN111133203B/zh active Active
- 2018-08-20 WO PCT/EP2018/072379 patent/WO2019057413A1/de unknown
- 2018-08-20 US US16/645,090 patent/US11225977B2/en active Active
Also Published As
Publication number | Publication date |
---|---|
EP3658781B1 (de) | 2023-01-11 |
EP3460256A1 (de) | 2019-03-27 |
JP7074957B2 (ja) | 2022-05-25 |
CN111133203B (zh) | 2021-03-09 |
CN111133203A (zh) | 2020-05-08 |
US20200284269A1 (en) | 2020-09-10 |
JP2020534477A (ja) | 2020-11-26 |
WO2019057413A1 (de) | 2019-03-28 |
US11225977B2 (en) | 2022-01-18 |
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