EP3465056A1 - Heat exchanger tube - Google Patents
Heat exchanger tubeInfo
- Publication number
- EP3465056A1 EP3465056A1 EP17725859.7A EP17725859A EP3465056A1 EP 3465056 A1 EP3465056 A1 EP 3465056A1 EP 17725859 A EP17725859 A EP 17725859A EP 3465056 A1 EP3465056 A1 EP 3465056A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rib
- tube
- heat exchanger
- ribs
- projections
- 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
- 238000012546 transfer Methods 0.000 description 27
- 239000012530 fluid Substances 0.000 description 13
- 238000001704 evaporation Methods 0.000 description 6
- 230000008901 benefit Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 4
- 230000002441 reversible effect Effects 0.000 description 4
- 230000005494 condensation Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 238000013467 fragmentation Methods 0.000 description 1
- 238000006062 fragmentation reaction Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000006911 nucleation Effects 0.000 description 1
- 238000010899 nucleation Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000009751 slip forming Methods 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
- F28F1/16—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being integral with the element, e.g. formed by extrusion
- F28F1/18—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being integral with the element, e.g. formed by extrusion the element being built-up from finned sections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
- F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
- F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular element
Definitions
- Heat transfer tube The present invention relates to a heat transfer tube according to the preamble of claim 1.
- Heat transfer occurs in many areas of refrigeration and air conditioning technology as well as in process and energy technology.
- tube bundle heat exchangers are often used in these areas.
- a liquid flows on the inner side of the pipe, which is cooled or heated depending on the direction of the heat flow.
- the heat is released or withdrawn from the medium located on the tube outside.
- structured tubes are used instead of smooth tubes.
- the structures improve the heat transfer.
- the heat flow density is thereby increased and the heat exchanger can be made more compact.
- the heat flux density can be maintained and the driving temperature difference lowered, allowing more energy efficient heat transfer.
- One or both sides structured heat exchanger tubes for tube bundle heat exchangers usually have at least one structured area and smooth end pieces and possibly smooth spacers.
- the smooth end or intermediate pieces limit the structured areas.
- the outer diameter of the structured regions should not be greater than the outer diameter of the smooth end and intermediate pieces.
- integrally rolled finned tubes are often used. Integrally rolled finned tubes are understood to mean finned tubes in which the fins have been formed from the material of the wall of a smooth tube.
- finned tubes on the inside of the tube have a multiplicity of axially parallel or helically encircling ribs which increase the internal surface and improve the heat transfer coefficient on the inside of the tube.
- the finned tubes On the outside, the finned tubes have annular or helical circumferential ribs.
- many possibilities have been developed, depending on the application to further increase the heat transfer on the outside of integrally rolled finned tubes by providing the ribs on the outside of the tube with further structural features.
- the heat transfer coefficient is significantly increased in the case of condensation of refrigerants on the outside of the pipe when the rib flanks are provided with additional convex edges.
- the axially parallel or helically encircling inner ribs can be provided with grooves, as described in the document DE 101 56 374 C1 and DE 10 2006 008 083 B4. It is important that the dimensions of the inner and outer structures of the finned tube can be adjusted independently of one another by the use of profiled mandrels disclosed therein to produce the inner fins and grooves. This allows the structures on the outside and inside to be adapted to the respective requirements and thus the tube can be designed.
- the object of the present invention is to develop inner or outer structures of heat exchanger tubes of the aforementioned type so that a comparison with already known pipes, a further increase in performance is achieved.
- the invention includes a heat exchanger tube having a tube longitudinal axis, a tube wall, a tube outside and a tube inside, wherein formed on the tube outside and / or inside tube from the tube wall continuously extending, axially parallel or helically encircling ribs and continuously formed between each adjacent ribs extending primary grooves ,
- the ribs along the rib run are subdivided into periodically repeating rib sections which are divided into a plurality of projections having a protrusion height, the protrusions being formed by cutting the ribs with a cutting depth transverse to the rib run are formed by rib segments and by raising the rib segments with a main orientation along the rib course between primary grooves.
- the structured region can, in principle, be formed on the outside of the pipe or on the inside of the pipe.
- the rib sections according to the invention inside the tube.
- the structures described can be used for both evaporator and condenser tubes.
- the protrusion height is expediently defined as the dimension of a protrusion in the radial direction.
- the projection height is then in the radial direction, the distance from the pipe wall to the farthest from the pipe wall point of the projection.
- the cutting depth also called notch depth, is the distance measured in the radial direction, starting from the original rib tip to the lowest point of the notch.
- the notch depth is the difference between the original rib height and the residual rib height remaining at the lowest point of a notch.
- the invention is based on the consideration that the rib sections can in principle be formed on the outside of the pipe or the pipe inside. However, it is preferred to arrange the rib sections according to the invention inside the tube.
- the structures described can be used for both evaporator and condenser tubes.
- the rib sections according to the invention are particularly suitable for internal structures.
- the inner surface of the tube is enlarged with a plurality of projections, which are divided into rib sections.
- the tube-side heat transfer resistance is significantly reduced and the heat transfer coefficient is increased.
- the projections create additional Routes for fluid flow within the tube and thereby increase the turbulence of the heat transfer medium flowing within the tube. This measure reduces the boundary layer built up from the fluid near the inner surface of the tube.
- the protrusions provide a multiple of additional surface area for additional heat exchange.
- Experiments show that the performance of tubes with the specially designed rib sections of this invention is significantly increased.
- the process-side structuring of the heat exchanger tube according to the invention can be produced using a tool which has already been described in DE 603 17 506 T2.
- the disclosure of this document DE 603 17 506 12 is fully incorporated into the present documents.
- the projection height and the distance can be made variable and individually adapted to the requirements, for example, the viscosity of the liquid or the flow rate.
- the tool used has a cutting edge for cutting through the ribs on the inner surface of the tube to provide rib segments and a lifting edge for raising the rib segments to form the protrusions.
- the projections are formed without removal of metal from the inner surface of the tube.
- the protrusions on the inner surface of the tube may be formed in the same or different processing as the formation of the ribs.
- the solution according to the invention in which the ribs are divided into rib portions which are divided into a plurality of protrusions with a protrusion height, causes the protrusions to deviate from the controlled order.
- This results in an optimized heat transfer at the lowest possible pressure loss, since the fluid boundary layer, which is a hindrance to a good heat transfer, is interrupted by additionally generated turbulence.
- An interruption due to the fragmentation of the projections additionally leads to an increase in the turbulence and to a fluid exchange over the course of the primary rib, which likewise causes an interruption of the boundary layer.
- the structured region can, in principle, be formed on the outside of the pipe or on the inside of the pipe.
- the structures described can be used for both evaporator and condenser tubes.
- a homogeneous arrangement of the projections can afford this targeted interruption of the boundary layer only conditionally.
- the shapes, heights and arrangement of the distances can be adjusted and optimized by adjusting the cutting blades or cutting geometries and by individually adapted primary rib shapes and geometries.
- the shape of the projections can be adapted individually and thus the interruption of the boundary layer can be carried out efficiently.
- the rib portions of the ribs measured at a pitch angle ß secondary grooves measured against the tube longitudinal axis may be formed from the ribs.
- the secondary grooves with respect to the inner ribs at a pitch angle of at least 10 ° and at most 80 ° extend.
- the depth of the secondary grooves may vary and be at least 20% of the original rib height of the inner ribs.
- rib sections spaced apart from each other on the inner side of the tube form structural elements which are similar to truncated pyramids.
- the projections have alternately changing cutting depths through a rib.
- the height of the individual projections can be adapted and vary with each other, thus immersing the laminar flow through different rib heights into the different boundary layers of the flow up to the flow core and dissipating the heat to the pipe wall.
- the cutting or notching depth can extend through the entire original rib into the core wall.
- An alternating notch or cutting depth is synonymous with the fact that the respective lowest point of the notches alternates and consequently changes the distance to the pipe wall. It is also synonymous that the lowest point of the Notches - here called Kerbground - alternately at intervals from the tube longitudinal axis via successive notches in the rib direction.
- the notches adjacent to at least one projection in the notch depth can vary by at least 10%. More preferably, the variation of the notch depth can be at least 20% or even 50%.
- At least one projection can protrude from the main alignment along the rib course over the primary groove.
- the rib portions of the ribs along the rib course may be formed elongated.
- the ribs are divided into rib portions which are divided into a sufficient plurality of protrusions with a protrusion height.
- a rib section comprises at least 3, preferably at least 4 protrusions.
- the rib portions may be spaced from each other, thereby forming passage points for the fluid. This in turn results in an optimized heat transfer at the lowest possible pressure loss, since the fluid boundary layer, which is a hindrance to a good heat transfer, is interrupted by additionally generated turbulence. An interruption additionally leads to an increase in the turbulence and to a fluid exchange over the course of the primary rib, which likewise causes an interruption of the boundary layer.
- a plurality of projections at the remote from the pipe wall location have a parallel to the tube longitudinal axis surface.
- the projections in Projecting height, shape and orientation vary with each other to selectively adjust the height of the individual projections and to each other to dive so particularly in laminar flow through different rib heights in the different boundary layers of the flow up to the flow core and derive the heat to the pipe wall.
- a projection on the side facing away from the tube wall side have a pointed tip. This leads to condenser tubes with the use of two-phase fluids for an optimized condensation at the tip of the projection.
- a projection on the side facing away from the tube wall side have a curved tip whose local radius of curvature is reduced starting from the pipe wall with increasing distance.
- the projections may have a different shape and / or height of a pipe beginning along the pipe longitudinal axis towards the opposite pipe end.
- the advantage here is a targeted adjustment of the heat transfer from the pipe beginning to pipe end.
- the tips of at least two projections along touching or crossing each other over the course of the rib which is especially advantageous in reversible operation during phase change, since the projections for the liquefaction project far out of the condensate and form a kind of cavity for the evaporation.
- the tips of at least two projections over the primary groove can touch or cross one another. This is particularly advantageous in reversible operation during phase change, since the projections for the liquefaction project far out of the condensate and form a type of cavity for the evaporation.
- At least one of the projections may be deformed in such a way that its tip touches the tube inner side or the tube outer side. This is advantageous in particular in reversible operation during phase change, since the projections for liquefaction form a type of cavity and thus nucleation sites for the evaporation.
- the protrusions may be formed of ribs, wherein at least one of the ribs in at least one of rib height, fin distance, fin tip, fin clearance, fin opening angle, and twist varies from each other.
- FIG. 1 shows schematically an oblique view of a pipe section with the structure according to the invention on the inside of the pipe;
- FIG. 2 schematically shows a further oblique view of a pipe cutout with the inner structure according to the invention with secondary groove;
- FIG. 3 shows schematically a rib section with different notch depth;
- Fig. 4 shows schematically a rib portion with a collar over the primary groove
- Fig. 5 shows schematically a rib portion with a rib direction at the
- Fig. 6 shows schematically a rib portion with a projection with a parallel
- FIG. 7 shows schematically a rib section with two projections which contact one another along the rib course
- FIG. 8 shows schematically a rib section with two projections which cross each other along the course of the rib
- Fig. 10 shows schematically a rib section with two mutually crossing over the primary groove over projections.
- Fig. 1 shows schematically an oblique view of a pipe section of the heat exchanger tube 1 with the structure according to the invention on the tube inside 22.
- the heat exchanger tube 1 has a tube wall 2, a tube outside 21 and a tube inside 22.
- On the tube inside 22 are from the tube wall 2 continuously extending, helical encircling ribs 3 shaped.
- the tube longitudinal axis A runs opposite the ribs at a certain angle. Between each adjacent ribs 3 continuously extending primary grooves 4 are formed.
- the ribs 3 are divided along the rib course into periodically repeating rib sections 31, which are divided into a plurality of projections 6.
- the projections 6 are formed by cutting the ribs 3 with a cutting depth transverse to the rib run to form rib segments and lifting the rib segments with a primary orientation along the rib run between primary grooves 4.
- rib portions 31 of the ribs 3 along the rib course are formed elongated.
- a rib section 31 is delimited by an uncut portion of a rib 3 with respect to the following.
- the original height of the primary rib 3 may be partially preserved.
- FIG. 2 shows schematically a further oblique view of a tubular section of the heat exchanger tube 1 with the structure according to the invention on the inside of the tube 22 with secondary groove 5.
- the ribs 3 are in turn subdivided along the rib course into periodically repeating rib sections 31, which are divided into a plurality of projections 6 ,
- rib portions 31 of the ribs 3 are again elongated along the rib course.
- a rib portion 31 is opposite to the following by a running at a pitch angle ß secondary groove 5 measured against the pipe axis A from.
- the secondary groove 5 may have a low notch depth or, as in the exemplary embodiment shown, come close to the primary notch with a large notch depth.
- Fig. 3 shows schematically a rib portion 31 with different cutting or notch depth t- ⁇ , t 2 , t 3rd In the context of the invention, the terms “cutting depth” and "notching depth” represent the same terminology.
- the projections 6 have alternating cutting depths ti, t 2 , t 3 through a rib 3.
- the protrusion height h is shown in FIG. 2 as the dimension of a protrusion in the radial direction.
- the projection height h is then in the radial direction, the distance from the pipe wall to the farthest from the pipe wall point of the projection.
- the notch depth ti, t 2] t 3 is the distance measured in the radial direction, starting from the original rib tip to the lowest point of the notch. In other words.
- the notch depth is the difference between the original rib height and the residual rib height remaining at the lowest point of a notch.
- FIG. 4 schematically shows a rib section 31 with a structural element 6 projecting over the primary groove 4. This is a projection 6 which extends over the primary groove 4 from the main alignment with the tip 62 along the rib course. The further the protrusion is formed, the more intensively the formed boundary layer of the fluid in the rib space is disturbed, which causes an improved heat transfer.
- FIG. 5 schematically shows a rib portion 31 with a projection 6 which is curved in the rib direction at the tip 62.
- the projection 6 has a changing curvature profile at the curved tip 62.
- the local radius of curvature decreases starting from the pipe wall with increasing distance.
- the radius of curvature decreases along the line indicated by the points P1, P2, P3 to the tip 62.
- This has the advantage that the condensate formed at the tip 62 is transported faster in two-phase fluids by the increasing convex curvature towards the rib foot. This optimizes the heat transfer during liquefaction.
- FIG. 6 schematically shows a rib section 31 with a projection 6 with a parallel surface 61 at the point furthest away from the tube wall in the region of the tip 62.
- Fig. 7 shows schematically a rib section 31 with two projections 6 touching each other along the rib run. Furthermore, Fig. 8 shows schematically a rib section 31 with two projections 6 crossing each other along the course of the ribs. Fig. 9 also schematically shows a rib section 31 with two over the primary groove 4 of time mutually touching projections. FIG. 10 schematically shows a rib section 31 with two projections 6 which mutually cross over the primary groove 4.
- FIGS. 7 to 10 it is particularly advantageous in reversible operation in the case of two-phase fluids that they form a type of cavity for the evaporation.
- the cavities of this special type form the starting points for bubble nuclei of an evaporating fluid.
Landscapes
- Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Geometry (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102016006913.9A DE102016006913B4 (en) | 2016-06-01 | 2016-06-01 | heat exchanger tube |
PCT/EP2017/000597 WO2017207091A1 (en) | 2016-06-01 | 2017-05-17 | Heat exchanger tube |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3465056A1 true EP3465056A1 (en) | 2019-04-10 |
EP3465056B1 EP3465056B1 (en) | 2022-07-06 |
Family
ID=58772829
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17725859.7A Active EP3465056B1 (en) | 2016-06-01 | 2017-05-17 | Heat exchanger tube |
Country Status (10)
Country | Link |
---|---|
US (1) | US10948245B2 (en) |
EP (1) | EP3465056B1 (en) |
JP (1) | JP6907232B2 (en) |
KR (1) | KR102367602B1 (en) |
CN (1) | CN109312992A (en) |
DE (1) | DE102016006913B4 (en) |
MX (1) | MX2018014689A (en) |
PL (1) | PL3465056T3 (en) |
PT (1) | PT3465056T (en) |
WO (1) | WO2017207091A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20190293364A1 (en) * | 2018-03-22 | 2019-09-26 | Johnson Controls Technology Company | Varied geometry heat exchanger systems and methods |
CN109631623B (en) * | 2018-12-22 | 2020-12-08 | 大连尼维斯冷暖技术有限公司 | Fin heat exchanger manufactured by using string pipe jig |
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DE2808080C2 (en) | 1977-02-25 | 1982-12-30 | Furukawa Metals Co., Ltd., Tokyo | Heat transfer tube for boiling heat exchangers and process for its manufacture |
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DE4404357C2 (en) | 1994-02-11 | 1998-05-20 | Wieland Werke Ag | Heat exchange tube for condensing steam |
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JP3323682B2 (en) * | 1994-12-28 | 2002-09-09 | 株式会社日立製作所 | Heat transfer tube with internal cross groove for mixed refrigerant |
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DE19963353B4 (en) * | 1999-12-28 | 2004-05-27 | Wieland-Werke Ag | Heat exchanger tube structured on both sides and method for its production |
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DE10156374C1 (en) | 2001-11-16 | 2003-02-27 | Wieland Werke Ag | Heat exchange tube structured on both sides has inner fins crossed by secondary grooves at specified rise angle |
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2016
- 2016-06-01 DE DE102016006913.9A patent/DE102016006913B4/en active Active
-
2017
- 2017-05-17 MX MX2018014689A patent/MX2018014689A/en unknown
- 2017-05-17 EP EP17725859.7A patent/EP3465056B1/en active Active
- 2017-05-17 WO PCT/EP2017/000597 patent/WO2017207091A1/en unknown
- 2017-05-17 JP JP2018558389A patent/JP6907232B2/en active Active
- 2017-05-17 PL PL17725859.7T patent/PL3465056T3/en unknown
- 2017-05-17 CN CN201780034247.7A patent/CN109312992A/en active Pending
- 2017-05-17 US US16/099,271 patent/US10948245B2/en active Active
- 2017-05-17 KR KR1020187030836A patent/KR102367602B1/en active IP Right Grant
- 2017-05-17 PT PT177258597T patent/PT3465056T/en unknown
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DE102016006913A1 (en) | 2017-12-07 |
JP6907232B2 (en) | 2021-07-21 |
US20190145718A1 (en) | 2019-05-16 |
WO2017207091A1 (en) | 2017-12-07 |
KR20190013719A (en) | 2019-02-11 |
DE102016006913B4 (en) | 2019-01-03 |
MX2018014689A (en) | 2019-02-28 |
EP3465056B1 (en) | 2022-07-06 |
US10948245B2 (en) | 2021-03-16 |
PT3465056T (en) | 2022-08-22 |
KR102367602B1 (en) | 2022-02-25 |
JP2019517650A (en) | 2019-06-24 |
CN109312992A (en) | 2019-02-05 |
PL3465056T3 (en) | 2022-11-14 |
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