EP3111153A1 - Metal heat exchanger tube - Google Patents
Metal heat exchanger tubeInfo
- Publication number
- EP3111153A1 EP3111153A1 EP15704718.4A EP15704718A EP3111153A1 EP 3111153 A1 EP3111153 A1 EP 3111153A1 EP 15704718 A EP15704718 A EP 15704718A EP 3111153 A1 EP3111153 A1 EP 3111153A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- channel
- heat exchanger
- exchanger tube
- additional structures
- ribs
- 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
- 239000002184 metal Substances 0.000 title abstract 2
- 239000012530 fluid Substances 0.000 claims abstract description 13
- 239000000463 material Substances 0.000 claims description 15
- 239000007788 liquid Substances 0.000 description 21
- 238000001704 evaporation Methods 0.000 description 15
- 230000008020 evaporation Effects 0.000 description 15
- 238000000034 method Methods 0.000 description 13
- 239000011148 porous material Substances 0.000 description 10
- 230000008569 process Effects 0.000 description 10
- 238000012546 transfer Methods 0.000 description 10
- 230000015572 biosynthetic process Effects 0.000 description 7
- 230000011218 segmentation Effects 0.000 description 5
- 230000002349 favourable effect Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 230000006911 nucleation Effects 0.000 description 2
- 238000010899 nucleation Methods 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- 101100334009 Caenorhabditis elegans rib-2 gene Proteins 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000009835 boiling Methods 0.000 description 1
- 239000012267 brine Substances 0.000 description 1
- 230000005587 bubbling Effects 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000001419 dependent effect Effects 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
- 230000035784 germination Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 230000005012 migration Effects 0.000 description 1
- 238000013508 migration Methods 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000003252 repetitive effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- HPALAKNZSZLMCH-UHFFFAOYSA-M sodium;chloride;hydrate Chemical compound O.[Na+].[Cl-] HPALAKNZSZLMCH-UHFFFAOYSA-M 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 239000010409 thin film Substances 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
- 230000008016 vaporization Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
- F28F1/12—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
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0017—Flooded core heat exchangers
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
- F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
- F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
- F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/02—Details of evaporators
- F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
- F25B2339/0242—Evaporators with refrigerant in a vessel in which is situated a heat exchanger having tubular elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
- F28D2021/0064—Vaporizers, e.g. evaporators
Definitions
- the invention relates to a metallic heat exchanger tube after the
- Evaporation occurs in many areas of refrigeration and air conditioning technology as well as in process and energy technology.
- shell-and-tube heat exchangers are used in which liquids of pure substances or mixtures evaporate on the outside of the pipe, cooling a brine or water on the inside of the pipe.
- Such apparatus are called flooded evaporators
- Evaporators have on the tube outside a rib structure with a rib density of 55 to 60 ribs per inch (US 5,669,441 A, US 5,697,430 A, DE 197 57 526 C1). This corresponds to a rib pitch of about 0.45 to 0.40 mm. Furthermore, it is known that performance-enhanced evaporation structures can be produced with the same fin pitch on the outside of the tube by introducing additional structural elements in the region of the groove bottom between the ribs.
- EP 1 223 400 B1 it is proposed to produce undercut secondary grooves on the groove bottom between the ribs which extend continuously along the primary groove.
- the cross section of these secondary grooves can remain constant or varied at regular intervals.
- DE 10 2008 013 929 B3 discloses structures on the groove base which are designed as local cavities, whereby the process of bubbling is intensified in order to increase the heat transfer during the evaporation.
- the location of the cavities in the vicinity of the primary groove bottom is favorable for the evaporation process, since the excess temperature is greatest at the bottom of the groove and therefore the highest driving temperature difference is available there for bubble formation.
- the invention has the object of developing a performance-enhanced heat exchanger tube for the evaporation of liquids on the outside of the tube.
- the invention is represented by the features of claim 1.
- the other dependent claims relate to advantageous embodiments and further developments of the invention.
- the invention includes a metallic heat exchanger tube having integrally formed ribs, rib flanks and fin tip integral ribs on the tube exterior, the fin root being substantially radially remote from the ribs
- Additional structures divide the channel between the ribs into segments.
- the additional structures locally reduce the flow-through cross-sectional area in the channel between two ribs by at least 60% and at least limit a fluid flow in the channel during operation.
- These metallic heat exchanger tubes are used in particular for
- Integrally rolled finned tubes are understood to mean finned tubes in which the fins are formed from the wall material of a smooth tube.
- Typical integral ribs formed on the outside of the pipe are, for example, spirally encircling and have a ribbed foot, rib flanks and fin tip, the ribbed foot being in the
- the number of ribs is determined by counting successive bulges in the axial direction of a tube.
- the invention is based on the consideration that to increase the
- Additional structures is segmented.
- the additional structures can be formed at least partially from material of the pipe wall solid from the channel bottom.
- the additional structures are preferably arranged at regular intervals, starting from the channel base and extend transversely to
- the additional structures can extend radially from the rib foot to the rib flank and beyond.
- the additional structures extend, starting from the channel bottom, for example, as massive material projections transversely to the primary groove and separate them, as a weir as only partially überströmbare cross-barrier, into individual segments.
- the primary gut as a channel is at least partially subdivided at regular intervals starting from the channel base.
- the evaporator tube structures can be optimized in a targeted manner as a function of the application parameters by a targeted choice of the channel segmentation, whereby an increase of the heat transfer is achieved. Since the temperature of the rib foot is higher in the region of the groove bottom than at the rib tip, structural elements for intensifying the formation of bubbles in the groove base are also particularly effective.
- the evaporator tube structures can be further optimized depending on the application parameters to increase the heat transfer.
- the channel may be terminated radially outwardly except for individual local openings.
- the ribs may have a substantially T-shaped or ⁇ -shaped cross-section, whereby the channel between the ribs is closed except for pores as local openings. Through these openings, the resulting vapor bubbles in the evaporation process can escape.
- the deformation of the rib tips is done with methods that can be found in the prior art.
- Heat transfer coefficient of the structure a consistently high level.
- At least one local opening per segment may be present. This minimum requirement still ensures that during the evaporation process in a channel segment resulting
- the quotient of the number of local openings to the number of segments can be 1: 1 to 6: 1. Further preferred may this quotient is 1: 1 to 3: 1.
- the channels located between the ribs are substantially by material of the upper rib areas
- openings can also be designed as pores, which can be designed in the same size or in two or more size classes. In a ratio in which a plurality of local openings are formed on a segment, especially pores with two size classes may be suitable.
- each channel is followed by a large opening along the channels. This structure creates a directional flow in the channels. Liquid is preferentially drawn through the small pores with the aid of capillary pressure and wets the channel walls, producing thin films. The vapor accumulates in the center of the channel and escapes at the lowest capillary pressure points.
- the large pores must be dimensioned so that the steam can escape sufficiently quickly and the channels do not dry out.
- the first additional structures may be outwardly projecting radially outward protrusions from the channel bottom. This will also the
- Additional structures may be formed at least from material of the channel bottom between two integrally encircling ribs. This leaves a cohesive Get a connection for a good heat exchange from the pipe wall into the respective structural elements.
- the segmentation of the channel from a uniform material of the channel bottom is particularly favorable for the evaporation process.
- the first additional structures formed from the channel base can have a height between 0.15 and 1 mm
- High-performance finned tubes are particularly well matched and express that the structure sizes of the outer structures are preferably in the submillimeter to millimeter range.
- Additional structures may be formed at least from the rib edges of the integrally circumferential ribs on lateral projections. This may be performed alternatively or in addition to further projections from the channel base material.
- Additional structures should be formed at least from a rib from the rib tip, starting in the direction of the channel bottom. Consequently, the channel can also be tapered or completely closed by a desired amount from a combination of several complementary structural elements from below and / or from the side and / or from above. In any case, so that the channel between the ribs is divided into discrete segments.
- additional structures can be introduced at least partially via additional material. Additional material may be in nature and in relation to the interaction with the
- the additional structures may be asymmetric in shape
- the asymmetry of the structures appears here in a plane perpendicular to the tube axis cutting plane. Asymmetrical shapes, especially if a larger surface is formed, can make an additional contribution to the evaporation process. The asymmetry can be pronounced both at additional structures at the channel bottom as well as at the rib tip.
- the additional structures can have a trapezoidal cross section in a sectional plane running perpendicular to the tube axis. Trapezoidal cross-sections are technologically easy to control in the context of integrally rolled ribbed tube structures
- the respective reduced by cross-sectional structures, istströmbare cross-sectional area in the channel between two ribs vary.
- more or less continuous areas can be created locally in the channel.
- Fig. 1 shows schematically a partial view of a cross section of a
- Fig. 2 shows schematically a partial view of a cross section of another
- Heat exchanger tube with varied additional structures in the area of the fin tip
- Fig. 3 shows schematically a partial view of a cross section of a
- FIG. 1 shows schematically a partial view of a cross section of a heat exchanger tube 1 according to the invention with segments 8 subdivided by additional structures 7.
- the integrally rolled heat exchanger tube 1 has spirally encircling ribs 2 on the outside of the tube, between which a primary groove is formed as channel 6.
- the ribs 2 extend continuously without interruption along a helix line on the tube outside.
- the ribbed foot 3 projects essentially radially from the tube wall 10.
- Rib height H is measured on the finished heat exchanger tube 1 from the lowest point of the channel base 61, starting from the ribbed foot 3 over the rib flank 4, to the fin tip 5 of the completely shaped finned tube. It is proposed a heat exchanger tube 1, wherein in the region of the channel bottom 61, an additional structure 7 in the form of massive
- Projections 71 is arranged. These projections 71 are the first
- Channel bottom 61 formed.
- the solid projections 71 are arranged at preferably regular intervals in the channel base 61 and extend transversely to the channel profile of a fin 3 of a rib 2 for in the plane of the figure not shown above next rib foot.
- the primary groove is at least partially tapered as a channel 6 at regular intervals.
- the resulting segment 8 favors a
- Bubble nucleation in a special way. The exchange of liquid and vapor between the individual segments 8 is thereby reduced.
- the rib tips 5 are deformed as a distal region of the ribs 2 in such a way that they partly close the channel 6 in the radial direction as a further second additional structure 72.
- the connection between the channel 6 and the environment is configured in the form of pores 9 as local openings, so that steam bubbles can escape from the channel 6.
- Rib tips 5 is done with methods that can be found in the prior art.
- the primary grooves 6 in this way represent undercut grooves.
- the combination of the first and second additional structures 71 and 72 according to the invention results in a segment 8 in the form of a cavity which is further characterized in that it over a very wide range of operating conditions a very high performance in evaporation of liquids.
- the liquid evaporates within the segment 8.
- the resulting vapor exits the channel 6 at the local openings 9, through which liquid fluid also flows.
- wettable pipe surfaces can be of help.
- FIG. 2 shows schematically a partial view of a cross section of another heat exchanger tube 1 with varied second additional structures 72 in the area of the rib tip 5.
- the rib tips 5 are deformed as a distal region of the ribs 2 such that they partially close the channel 6 in the radial direction as a further second additional structure 72.
- the connection between the channel 6 and the environment is in the form of inclined tubes as local openings 9 designed for the escape of vapor bubbles from the channel 6 and inflow of liquid fluid into the channel 6.
- the primary grooves 6 are in this way again undercut grooves.
- Additional structure 72 is formed starting from a rib of the rib tip 5 in the direction of the channel base 61 out and so protrudes into the channel 6 in the radial direction. As soon as a first and a second additional structure overlap one another radially, the through-flow cross-sectional area in the channel 6 between two ribs 2 is locally particularly effectively reduced, thereby limiting the fluid flow in the channel 6 during operation.
- Fig. 3 shows schematically a partial view of a cross section of a heat exchanger tube 1 with the additional structures 7 of Fig. 2.
- Additional structures 72 protrude almost to the projections of the first
- the quotient of the number of local openings 9 to the number of segments 8 in the preferred interval is 1: 1 to 3: 1 and is on average about 1.7: 1 to 2.3: 1.
- all are tubes
- first and second additional structures 71 and 72 results in a segment 8 in the form of a cavity, which is further characterized in that it has a very wide range of
- the inventive Solution refers to structured pipes where the heat transfer coefficient on the outside of the pipe is increased. In order not to relocate the majority of the heat transfer resistance to the inside, the heat transfer coefficient on the inside by a suitable
- Interior structuring 1 1 also be intensified.
- the heat exchanger tubes 1 for shell and tube heat exchangers usually have at least one structured region and smooth end pieces and possibly smooth ones
- the heat exchanger tube 1 can be easily installed in the tube bundle heat exchanger, the outer
- Diameter of the structured areas should not be greater than the outer one
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Chemical & Material Sciences (AREA)
- Crystallography & Structural Chemistry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PL15704718T PL3111153T3 (en) | 2014-02-27 | 2015-02-10 | Metal heat exchanger tube |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014002829.1A DE102014002829A1 (en) | 2014-02-27 | 2014-02-27 | Metallic heat exchanger tube |
PCT/EP2015/000278 WO2015128061A1 (en) | 2014-02-27 | 2015-02-10 | Metal heat exchanger tube |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3111153A1 true EP3111153A1 (en) | 2017-01-04 |
EP3111153B1 EP3111153B1 (en) | 2019-04-24 |
Family
ID=52473867
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15704718.4A Active EP3111153B1 (en) | 2014-02-27 | 2015-02-10 | Metal heat exchanger tube |
Country Status (13)
Country | Link |
---|---|
US (1) | US11073343B2 (en) |
EP (1) | EP3111153B1 (en) |
JP (1) | JP6197121B2 (en) |
KR (1) | KR102367582B1 (en) |
CN (1) | CN106030233B (en) |
BR (1) | BR112016019767B1 (en) |
DE (1) | DE102014002829A1 (en) |
HU (1) | HUE044830T2 (en) |
MX (1) | MX2016006294A (en) |
PL (1) | PL3111153T3 (en) |
PT (1) | PT3111153T (en) |
TR (1) | TR201906855T4 (en) |
WO (1) | WO2015128061A1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107421160B (en) * | 2017-08-28 | 2020-11-10 | 华北电力大学(保定) | High-efficient controllable cooling device |
JP2023545916A (en) * | 2020-10-31 | 2023-11-01 | ヴィーラント ウェルケ アクチーエン ゲゼルシャフト | metal heat exchanger tube |
DE202020005625U1 (en) | 2020-10-31 | 2021-11-10 | Wieland-Werke Aktiengesellschaft | Metallic heat exchanger tube |
DE202020005628U1 (en) | 2020-10-31 | 2021-11-11 | Wieland-Werke Aktiengesellschaft | Metallic heat exchanger tube |
CN116507864A (en) * | 2020-10-31 | 2023-07-28 | 威兰德-沃克公开股份有限公司 | Metal heat exchanger tube |
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-
2014
- 2014-02-27 DE DE102014002829.1A patent/DE102014002829A1/en not_active Withdrawn
-
2015
- 2015-02-10 PL PL15704718T patent/PL3111153T3/en unknown
- 2015-02-10 TR TR2019/06855T patent/TR201906855T4/en unknown
- 2015-02-10 EP EP15704718.4A patent/EP3111153B1/en active Active
- 2015-02-10 WO PCT/EP2015/000278 patent/WO2015128061A1/en active Application Filing
- 2015-02-10 MX MX2016006294A patent/MX2016006294A/en active IP Right Grant
- 2015-02-10 KR KR1020167014382A patent/KR102367582B1/en active IP Right Grant
- 2015-02-10 US US15/103,193 patent/US11073343B2/en active Active
- 2015-02-10 BR BR112016019767-4A patent/BR112016019767B1/en active IP Right Grant
- 2015-02-10 HU HUE15704718 patent/HUE044830T2/en unknown
- 2015-02-10 CN CN201580002855.0A patent/CN106030233B/en active Active
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Also Published As
Publication number | Publication date |
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KR102367582B1 (en) | 2022-02-25 |
MX2016006294A (en) | 2016-12-08 |
DE102014002829A1 (en) | 2015-08-27 |
HUE044830T2 (en) | 2019-11-28 |
WO2015128061A1 (en) | 2015-09-03 |
KR20160125348A (en) | 2016-10-31 |
US20160305717A1 (en) | 2016-10-20 |
CN106030233A (en) | 2016-10-12 |
EP3111153B1 (en) | 2019-04-24 |
BR112016019767A2 (en) | 2017-10-24 |
US11073343B2 (en) | 2021-07-27 |
JP2017501362A (en) | 2017-01-12 |
BR112016019767B1 (en) | 2020-12-08 |
CN106030233B (en) | 2019-06-21 |
PL3111153T3 (en) | 2019-09-30 |
TR201906855T4 (en) | 2019-05-21 |
PT3111153T (en) | 2019-07-30 |
JP6197121B2 (en) | 2017-09-13 |
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