EP3009684B1 - Ventilator für trockenkühler - Google Patents

Ventilator für trockenkühler Download PDF

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Publication number
EP3009684B1
EP3009684B1 EP15183722.6A EP15183722A EP3009684B1 EP 3009684 B1 EP3009684 B1 EP 3009684B1 EP 15183722 A EP15183722 A EP 15183722A EP 3009684 B1 EP3009684 B1 EP 3009684B1
Authority
EP
European Patent Office
Prior art keywords
blade
fan
blades
pressure
hub
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.)
Active
Application number
EP15183722.6A
Other languages
English (en)
French (fr)
Other versions
EP3009684A1 (de
Inventor
Jacques Arnold
Aurélien Deruelle
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kelvion Thermal Solutions
Original Assignee
Kelvion Thermal Solutions SAS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kelvion Thermal Solutions SAS filed Critical Kelvion Thermal Solutions SAS
Priority to PL15183722T priority Critical patent/PL3009684T3/pl
Publication of EP3009684A1 publication Critical patent/EP3009684A1/de
Application granted granted Critical
Publication of EP3009684B1 publication Critical patent/EP3009684B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F04D25/166—Combinations of two or more pumps ; Producing two or more separate gas flows using fans
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/023—Selection of particular materials especially adapted for elastic fluid pumps
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/34—Blade mountings
    • F04D29/36—Blade mountings adjustable
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/43—Synthetic polymers, e.g. plastics; Rubber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/60—Properties or characteristics given to material by treatment or manufacturing
    • F05D2300/603—Composites; e.g. fibre-reinforced

Definitions

  • the invention relates to an industrial ventilator for aero-refrigerant, comprising a disk-shaped hub and a plurality of blades radially connected to the disk of the hub via a stud provided on one end of each blade and a flange. provided on a face of the hub and in which is inserted the bolt of the blade.
  • Such a fan is for example used for the oil, gas and chemical industries.
  • it can be used in an air heat exchanger to condense and cool liquids, such as liquefied natural gas, that circulate in finned tube bundles.
  • the finned tube bundles are installed on a structure and are blown by one or more such fans powered by electric motors.
  • Such an industrial fan is in particular disclosed in the patent document WO-2011/126568 . It can have large dimensions, the diameter of the rotor often exceeding 2 meters so that the blades are in practice mounted on the disk-shaped hub.
  • the blade angle for each blade is set to a value between 25 ° and 45 ° when designing the heat exchanger, with a tolerance of +/- 1 °.
  • the efficiency of a fan can be affected by an air recirculation phenomenon that can occur at the base of each blade when there is sufficient free space between the hub and the fan. base of the blades to let air circulate which passes from the intrados of the blade towards the extrados of the blade.
  • the overall efficiency of the fan is reduced because the air velocity profile is not homogeneous. Because of this air recirculation phenomenon, about one-third of the blade surface can not be charged with air and is rendered useless.
  • Patent publication US 2003/0077172 describes a fan in which fins are placed at the ends of the blades and allow to eliminate these vortices by creating a barrier between the low pressure and the high pressure on the sides of the end of a blade.
  • a complexity in the geometry of the blades can be a track to reduce the noise generated by the fan.
  • the blades can thus have a complex structure such as a curvature of the leading and trailing edges, in particular having leading edges having an arrow angle before the ends of the blades relative to the radial direction. Curvatures before attack edges are used to desynchronize the sources of noise along the blades but do not reduce the noise source itself. In addition, it makes the flow of air around the blade unstable and thus reduces their efficiency.
  • WO-2011/126568 discloses a fan with blades which each have a substantially rectilinear leading edge and trailing edge. This simplified blade shape has surprisingly shown that it contributes to reducing the operating noise of the fan. However, this fan does not limit the recirculation of the air flow around the hub and thus does not have optimum efficiency.
  • the object of the invention is to remedy these disadvantages by proposing an industrial fan which has good mechanical strength with improved flow efficiency and which makes no noise.
  • the subject of the invention is an industrial fan for a dry cooler with the features of claim 1, the fan comprising a disc-shaped hub and a plurality of blades radially connected to the hub via a stud provided on one end of each of the blades and a flange provided on a face of the hub and in which is inserted the stud of the blade with a blade angle to produce an axial air flow, characterized in that each blade has an aerodynamic profile such that the pressure difference between intrados and extrados is between 65% and 75% over an area at 30% of the length of the blade from the blade root relative to the pressure difference between intrados and extrados in the middle of the blade rope and such that the pressure difference between the lower and upper surfaces is between 125% and 135% over an area at 30% of the blade length from the blade head by pport at the difference of pressure between intrados and extrados in mid-rope of blade, and in that it is provided a system of joint to block the recirculation of air between the intrados and the extrado
  • the fan according to the invention has a blade profile much more worked at the blade root which gives the blades an aerodynamic profile improving the performance of the industrial fan. Further with this stud / flange arrangement, the radial position and the pitch angle of the blades can be adjusted independently and easily by the ratio to the hub.
  • the joining means fills the space between the hub and the base of the blades, thus increasing the efficiency of the fan by limiting the recirculation of the air at the bottom of the blade.
  • the invention extends to a finned tube air heat exchanger characterized in that it comprises a fan according to the invention.
  • an air heat exchanger 1 condenses and cools liquids that circulate in finned tube bundles 2.
  • the finned tube bundles 2 are installed on an air heat exchanger 1. structure and they are blown by one or more fans 3 actuated by electric motors 4.
  • the figure 2 illustrates an industrial fan 3 for air cooler according to the state of the art.
  • This fan 3 comprises a disk-shaped hub 5 and a plurality of blades 6 radially connected to the disc of the hub 5 by means of a stud 7 provided on one end of each blade 6 and a flange (not shown schematically). provided on a face of the disc of the hub 5 and in which is inserted the stud 7 of the blade 6 with a blade angle to produce an axial air flow.
  • the arrow F indicates the direction of rotation of the blades 6.
  • the blades 6 have a curvature of the leading and trailing edges, in particular the leading edges have an angle of deflection before the ends of the blades relative to the radial direction.
  • Free spaces are visible between the hub 5 and the base of the blades 6. These spaces induce a recirculation of the air flow at the base of the blade 6 from the intrados to the extrados. This recirculation of air contributes to a decrease in the pressure on the blade 6 and a decrease in the speed of the air in the zone at the base of the blade 6. Without means of joining between the hub 5 and the base of the blades 6 blades, about one third of the surface of the blade 6 can not be loaded with air and is rendered useless. As the air velocity profile is not homogeneous, the overall efficiency of the fan 3 is reduced.
  • the figure 3 is a perspective view of a fan according to the invention, having a finned joining means 8 arranged at the base of the blades 6 to block the recirculation of air between the intrados and the extrados at the foot of the blade. On each blade, the fin extends along the pressure and the extrados perpendicularly to the surface of the blade 6 at the foot of the blade 6.
  • the joining means 8 has a form of revolution.
  • the joining means can be combined with sealing elements such as elastomer or silicone gaskets.
  • the fan 1 comprises in the case of example a disk-shaped flat hub 5 bearing on its lower surface in the direction of the air four blades 6.
  • the blades 6 extend radially between a blade base at the hub 5 and a blade head. They have a simplified form. Indeed each blade has a leading edge opposite a trailing edge which are both straight. The centroids of all sections along the blade 6 are perfectly aligned. Due to their simplified form, the manufacturing costs of the blades 6 are reduced.
  • the fans 3 according to the invention comprise at least three blades 6.
  • the length l of the blade 6 is divided by dotted lines into three zones, in particular an area at 30% of the length of the blade from the blade root, an area at 30% of the length of the blade from the blade head, and an area in the middle of the blade's rope. On each of these zones and at different points, pressure measurements between the intrados and extrados are carried out.
  • each of the blades 6 has an aerodynamic profile such as the pressure difference ( ⁇ P1) between intrados and extrados is between 65% and 75% over an area at 30% of the blade length from the blade root with respect to the pressure difference ( ⁇ PC) between intrados and extrados in the middle of blade rope and such that the pressure difference ( ⁇ P2) between the lower and upper surfaces is between 125% and 135% over an area at 30% of the blade length from the blade head with respect to the difference in pressure ( ⁇ PC) between intrados and extrados in mid-rope of blade.
  • ⁇ P1 pressure difference between intrados and extrados
  • ⁇ PC pressure difference between intrados and extrados in the middle of blade rope
  • each blade 6 has an aerodynamic profile as visible on the Figure 3 with a greater wedging angle at the blade root than at the blade tip, which makes it possible to have a more uniform pressure along the rope of the blade 6.
  • the figure 4 illustrates the connection between the hub 5 and a blade 6.
  • a stud 7 extends from the base of the blades and is fixed on a transverse wall 9 closing the blade root. This stud 7 makes it possible to attach the blades 6 on the underside of the disc of the hub 5 by means of a flange 10 fixed to the hub 5.
  • this flange 10 comprises at least one jaw.
  • this flange 10 comprises two jaws 10a, 10b fixed on the underside of the hub 5. As visible on the Figure 4 , the stud 7 of a blade 6 is housed in the two jaws 10a, 10b.
  • the wedging of the blade angle is adjustable between 25 ° and 45 °.
  • the angle of calibration is optimum calculated is about 36 °. It can be adjusted using an inclinometer. This inclinometer can be disposed on a perfectly flat area of the intrados surface of the blade. The pitch between the inclination angles of the blades 6 can thus be adjusted with an accuracy of + or - 0.1 °.
  • the fan can be supplied in parts and assembled on site. It is no longer necessary to manufacture a fan in one piece, for example by molding a hub 5 with the blades 6, which can be bulky to carry and also not adjustable on site. Often the adjustment of the angle of setting is necessary in order to be able to adjust the air flow on site or to increase the performance of the heat exchanger in the future.
  • the envelope of the blades can be made of composite materials, in the form of a premodelable fabric with a fiber reinforcement.
  • This fiber reinforcement can be glass fabric.
  • this envelope is impregnated with a two-component material with hardening such as polyester, vinyl esters, epoxides or the like. It is also possible that the coating is injection molded.
  • the blades 6 can be hollow. They can be stiffened by filling the cavity with a light material such as a polyurethane foam. Due to their lightened structure, the blades are easier to install.
  • a fan according to the invention at least 4 meters in diameter was produced and tested. This fan has been shown to have better performance and noise reduction than a "Super Low Noise” fan. In addition, due to the high aerodynamic efficiency of the fan according to the invention, a low operating speed is necessary and thus the production of noise remains limited.
  • the fan according to the invention provides even better performance while emitting as much sound as a device of the prior art. It has been shown that such a fan also has better performance while consuming less power than a fan of the prior art.
  • the invention extends to an air heat exchanger 1 with finned tubes 2 comprising a fan 3 according to the invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (15)

  1. Industrieventilator (3) für Luftkühlmittel, umfassend eine scheibenförmige Nabe (5) und eine Mehrzahl von Schaufeln (6), die radial mit der Nabe (5) verbunden sind mittels eines an einem Ende jeder der Schaufeln (6) vorgesehenen Bolzens (7) und einer auf einer Seite der Nabe (5) vorgesehen Lasche (10), in die der Bolzen (7) der Schaufel (6) mit einem Schaufelwinkel eingesetzt ist, um einen axialen Luftfluss zu erzeugen,
    dadurch gekennzeichnet,
    dass jede der Schaufeln (6) ein aerodynamisches Profil aufweist derart, dass die Druckdifferenz (ΔP1) zwischen innerer Wölbfläche und äußerer Wölbfläche umfasst ist zwischen 65% und 75% über eine Zone von 30% der Länge der Schaufel (6), ausgehend von dem Fuß der Schaufel, in Bezug auf die Druckdifferenz (ΔPC) zwischen innerer Wölbfläche und äußerer Wölbfläche in der Segmentmitte der Spannweite der Schaufel (6) und derart, dass die Druckdifferenz (ΔP2) zwischen innerer Wölbfläche und äußerer Wölbfläche umfasst ist zwischen 125% und 135% über eine Zone von 30% der Länge der Schaufel (6) ausgehend von dem Kopf der Schaufel (6) in Bezug auf die Druckdifferenz (ΔPC) zwischen innerer Wölbfläche und äußerer Wölbfläche in der Segmentmitte der Spannweite der Schaufel (6), und
    dass ein Verbindungsmittel (8) zum Blockieren der Rezirkulation von Luft zwischen der inneren Wölbfläche und der äußeren Wölbfläche am Fuß der Schaufel vorgesehen ist.
  2. Ventilator (3) nach Anspruch 1, dadurch gekennzeichnet, dass das Verbindungsmittel (8) ein Flügel ist, der sich längs der inneren Wölbfläche und der äußeren Wölbfläche senkrecht zu der Fläche der Schaufel (6) am Fuß der Schaufel (6) erstreckt.
  3. Ventilator (3) nach Anspruch 1, dadurch gekennzeichnet, dass die Lasche (10) wenigstens eine Backe umfasst.
  4. Ventilator (3) nach Anspruch 1, dadurch gekennzeichnet, dass er wenigstens drei Schaufeln (6) umfasst.
  5. Ventilator (3) nach Anspruch 1, dadurch gekennzeichnet, dass die Hülle der Schaufeln (6) aus Verbundmaterialien ist.
  6. Ventilator (3) nach Anspruch 1, dadurch gekennzeichnet, dass die Hülle der Schaufeln (6) die Gestalt eines vormodellierbaren Stoffes mit einer Faserverstärkung aufweist.
  7. Ventilator (3) nach Anspruch 6, dadurch gekennzeichnet, dass die Faserverstärkung ein Glasfasergewebe ist.
  8. Ventilator (3) nach Anspruch 5, dadurch gekennzeichnet, dass die Hülle der Schaufeln (6) mit einem Material aus zwei Komponenten imprägniert ist, wie Polyester, Vinylester, Epoxide oder vergleichbare.
  9. Ventilator (3) nach einem der Ansprüche 5 bis 8, dadurch gekennzeichnet, dass dessen Überzug durch Spritzformen hergestellt ist.
  10. Ventilator (3) nach einem der vorgehenden Ansprüche, dadurch gekennzeichnet, dass die Schaufeln (6) hohl sind und durch Auffüllen ihres Hohlraums mit einem leichten Material wie einem Polyurethanschaum ausgesteift sind.
  11. Ventilator (3) nach Anspruch 1, dadurch gekennzeichnet, dass die Schaufeln (6) eine innere Wölbfläche aufweisen, die einen planen Oberflächenbereich aufweist, der geeignet ist, ein Neigungsmessgerät aufzunehmen, und dass die Schaufeln (6) einen anpassbaren Neigungswinkel aufweisen.
  12. Ventilator (3) nach Anspruch 1, dadurch gekennzeichnet, dass jede der Schaufeln (6) einen zwischen 25° und 45° anpassbaren Keilwinkel aufweisen.
  13. Ventilator (3) nach Anspruch 1, dadurch gekennzeichnet, dass die Position jeder der radial mit der Nabe (5) verbundenen Schaufeln (6) durch eine Schraube anpassbar ist.
  14. Ventilator (3) nach Anspruch 1, dadurch gekennzeichnet, dass das Verbindungsmittel (8) ein Rotationskörper ist und mit Abdichtungsmitteln wie Elastomer- oder Silikondichtungen kombiniert ist.
  15. Wärmetauscher (1) mit Luft, mit Rohren, mit Flügeln (2), dadurch gekennzeichnet, dass er einen Ventilator (3) nach einem der vorhergehenden Ansprüche umfasst.
EP15183722.6A 2014-09-11 2015-09-03 Ventilator für trockenkühler Active EP3009684B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL15183722T PL3009684T3 (pl) 2014-09-11 2015-09-03 Wentylator do chłodnicy powietrznej

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1458534A FR3025748B1 (fr) 2014-09-11 2014-09-11 Ventilateur pour aerorefrigerant.

Publications (2)

Publication Number Publication Date
EP3009684A1 EP3009684A1 (de) 2016-04-20
EP3009684B1 true EP3009684B1 (de) 2017-06-28

Family

ID=51987328

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15183722.6A Active EP3009684B1 (de) 2014-09-11 2015-09-03 Ventilator für trockenkühler

Country Status (6)

Country Link
US (1) US20160076546A1 (de)
EP (1) EP3009684B1 (de)
BR (1) BR102015021916A2 (de)
ES (1) ES2644810T3 (de)
FR (1) FR3025748B1 (de)
PL (1) PL3009684T3 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9618002B1 (en) * 2013-09-27 2017-04-11 University Of South Florida Mini notched turbine generator
JP6802270B2 (ja) * 2015-10-07 2020-12-16 ミネベアミツミ株式会社 インペラ、及び、そのインペラを備えた軸流ファン
US11391286B2 (en) * 2020-10-02 2022-07-19 Therma-Stor LLC Portable blower fan assembly

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Publication number Priority date Publication date Assignee Title
US2918977A (en) * 1956-06-25 1959-12-29 Koppers Co Inc Blade assembly
US3647317A (en) * 1970-03-19 1972-03-07 Fluor Prod Co Inc Fiberglass fan assembly
JPS5912197A (ja) * 1982-07-12 1984-01-21 Mitsubishi Heavy Ind Ltd 送風機の翼等の共振回避方法
US4971143A (en) * 1989-05-22 1990-11-20 Carrier Corporation Fan stator assembly for heat exchanger
US5564901A (en) * 1993-12-14 1996-10-15 The Moore Company Low noise fan
US6086330A (en) 1998-12-21 2000-07-11 Motorola, Inc. Low-noise, high-performance fan
ITMI991321A1 (it) * 1999-06-14 2000-12-14 Fbm Hudson Italiana Spa Pala svergolata per girante composta da due elementi congiunti
US6517315B2 (en) 2001-05-29 2003-02-11 Hewlett-Packard Company Enhanced performance fan with the use of winglets
US8672649B2 (en) * 2007-10-10 2014-03-18 Delta T Corporation Ceiling fan system with brushless motor
CN102947595B (zh) 2010-04-05 2016-10-12 穆尔风扇有限责任公司 包括包含超低噪音风扇叶片的轴流风扇的商业空气冷却装置

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Also Published As

Publication number Publication date
US20160076546A1 (en) 2016-03-17
ES2644810T3 (es) 2017-11-30
FR3025748A1 (fr) 2016-03-18
PL3009684T3 (pl) 2017-12-29
EP3009684A1 (de) 2016-04-20
FR3025748B1 (fr) 2016-11-18
BR102015021916A2 (pt) 2016-07-19

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