US20140318365A1 - Restrictor and production process of a fluid leakage restrictor for aerostatic bearings - Google Patents

Restrictor and production process of a fluid leakage restrictor for aerostatic bearings Download PDF

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Publication number
US20140318365A1
US20140318365A1 US14/358,623 US201214358623A US2014318365A1 US 20140318365 A1 US20140318365 A1 US 20140318365A1 US 201214358623 A US201214358623 A US 201214358623A US 2014318365 A1 US2014318365 A1 US 2014318365A1
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United States
Prior art keywords
restrictor
deformation
fluid
stage
production process
Prior art date
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Abandoned
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US14/358,623
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English (en)
Inventor
Henrique Bruggmann Muhle
Dietmar Erich Bernhard Lilie
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.)
Whirlpool SA
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Whirlpool SA
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Assigned to WHIRLPOOL S.A. reassignment WHIRLPOOL S.A. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LILIE, DIETMAR ERICH BERNHARD, MUHLE, HENRIQUE BRUGGMANN
Publication of US20140318365A1 publication Critical patent/US20140318365A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D31/00—Other methods for working sheet metal, metal tubes, metal profiles
    • B21D31/06—Deforming sheet metal, tubes or profiles by sequential impacts, e.g. hammering, beating, peen forming
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/122—Cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/126—Cylinder liners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/166—Cylinder liners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C29/00—Bearings for parts moving only linearly
    • F16C29/02—Sliding-contact bearings
    • F16C29/025—Hydrostatic or aerostatic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
    • F16C32/0614—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being supplied under pressure, e.g. aerostatic bearings
    • F16C32/0622—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being supplied under pressure, e.g. aerostatic bearings via nozzles, restrictors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49764—Method of mechanical manufacture with testing or indicating
    • Y10T29/49771—Quantitative measuring or gauging

Definitions

  • the present invention pertains to restrictors for aerostatic bearing of pistons in cylinders comprised by linear compressors for cooling.
  • the basic structure of a cooling circuit comprises four components, namely the compressor, the condenser, the expansion device and the evaporator. These elements characterize a cooling circuit in which a fluid circulates so as to allow the temperature of an internal environment to decrease, withdrawing the heat therefrom and displacing it to an external environment by way of the elements that make up the cooling circuit.
  • the fluid that circulates in the cooling circuit generally follows the passage sequence: compressor, condenser, expansion valve, evaporator and compressor again, thus characterizing a closed cycle.
  • the fluid undergoes variations of pressure and temperature which are responsible for changing the state of the fluid, which may be in gaseous or liquid state.
  • the compressor act as the heart of the cooling system, creating the flow of the cooling fluid along the system components.
  • the compressor raises the temperature of the cooling fluid by increasing the pressure provided on its inside and forces the circulation of this fluid in the circuit.
  • This bearing formation consists of the presence of a fluid in the gap between the external diameter of the piston and the internal diameter of the cylinder, preventing contact between them and the consequent premature wear and tear of the piston and/or cylinder.
  • the presence of the fluid between the two components referred to also serves to decrease attrition between them, meaning the mechanical loss of the compressor is minor.
  • One of the forms of piston bearing formation is by way of aerostatic bearings which, in essence, consists of creating a gas cushion between the piston and the cylinder so as to avoid wear and tear between these two components.
  • aerostatic bearings which, in essence, consists of creating a gas cushion between the piston and the cylinder so as to avoid wear and tear between these two components.
  • the gas has a much lower viscosity attrition coefficient than oil, contributing such that the energy dissipated in the aerostatic bearing formation system is much lower than that of a lubrication with oil, whereby achieving improved yield of the compressor.
  • the gas compression mechanism operates by the axial and oscillatory movement of a piston inside a cylinder.
  • the head At the top of the cylinder is the head, jointly with the piston and the cylinder forming a compression chamber.
  • the discharge and suction valves are positioned. These valves regulate the inflow and outflow of gas in the cylinder.
  • the piston is driven by an actuator which is connected to the linear motor of the compressor.
  • the piston of the compressor driven by the linear motor has the function of developing an alternative linear movement, meaning the movement of the piston inside the cylinder exerts a compression action on the gas let in by the suction valve, up to the point where it can be discharged to the high pressure side, through the discharge valve.
  • restricting the gas flow is dependent on the length and size of the internal diameter of the restrictor. For a certain size, the bigger the cross section to the gas flow, that is, the bigger the internal diameter, the lower the restriction imposed on the gas flow. Based on these two variables (cross section to the flow and length) it is possible to obtain a loss of load necessary for any bearing restrictor of the compressor.
  • microtubes available commercially on the market present very large tolerances in relation to the nominal internal diameter. This variation of the internal diameter may cause a very large variation in the restriction on gas flow and, consequently, of the flow between one restrictor and the other. This type of occurrence causes an imbalance in the bearing, chiefly if this variation occurs between restrictors present in the same section of the cylinder.
  • the present invention manages to achieve a production of restrictors that may differ from each other in terms of their dimensions, but that guarantee a same flow.
  • a further objective of the present invention is to provide restrictors for aerostatic bearings whose flow is adjusted by means of deformation of its internal section.
  • the objectives of the present invention are achieved by providing a flow restrictor tube of a fluid for aerostatic bearings, and the restrictor is obtained through a deformation process of at least a portion of its inner section.
  • the objectives of the present invention are also achieved by providing a flow restrictor of a fluid for aerostatic bearings of linear compressors, and the restrictor has at least a portion of its inner section deformed.
  • FIG. 1 is a cross-sectional view of a linear compressor.
  • FIG. 2 is a cross-sectional view of a restrictor of the state of the art.
  • FIG. 3 a is a cross-sectional view of restrictors of the present invention endowed with punctual constriction.
  • FIG. 3 b is a cross-sectional view of restrictors of the present invention endowed with partial constriction.
  • FIG. 3 c is a cross-sectional view of restrictors of the present invention endowed with total constriction.
  • FIG. 3 d is a cross-sectional view of restrictors of the present invention endowed with fold constriction.
  • FIG. 4 is a cross-sectional view of a constriction or kneading.
  • FIG. 5 is a cross-sectional view of restrictors of the present invention with combinations of types of kneading/constrictions and fold.
  • FIG. 6 is a view of an example of a system of regulating restrictors at rest.
  • FIG. 7 is a view of an example of a system of regulating restrictors at work.
  • the present invention proposes a technological advance both in the level of the restrictors (better known by persons skilled in the art as restrictor tubes/microtubes), as well as a productive process capable of producing the restrictors with the desired fluid flow characteristics.
  • the gas compression mechanism occurs by the axial and oscillatory movement of a piston 1 inside a cylinder 2 .
  • a head 3 which jointly with the piston 1 and the cylinder 2 form a compression chamber 4 .
  • the discharge 5 and suction 6 valves which regulate the inflow and outflow of gas in the cylinder 2 .
  • the piston 1 is driven by an actuator 7 linked to the linear motor of the compressor. No further explanations are provided on this motor in this document.
  • the piston 1 of a compressor when driven by the linear motor, has the function of developing an alternative linear movement, promoting a movement of the piston 1 inside the cylinder 2 which exerts compression action on the gas let in by the suction valve 6 up to the point where the gas can be discharged to the high pressure side, by way of the discharge valve 5 .
  • the cylinder 2 is mounted inside a block 8 and on the head 3 there is mounted a lid 9 with the drain valve 10 and the suction valve 11 , which connect the compressor to the rest of the system.
  • the relative movement between piston 1 and cylinder 2 , the bearing formation of the piston 1 is necessary, consisting of the presence of a fluid in the gap 12 between the two parts, with the purpose of separating them during movement.
  • An advantage of using the gas itself as lubricant fluid is the absence of an oil pumping system.
  • the gas used for the bearing formation can be the gas itself pumped by the compressor and used in the cooling system. Once compressed, this gas is diverted from the discharge chamber 13 , from the lid 9 through the channel 14 to the high pressure region 15 around the cylinder 2 , and the high pressure region 15 is formed by the external diameter of the cylinder 2 and internal diameter of the block 8 .
  • the gas passes through the restrictors 16 , 17 inserted in the wall of the cylinder 2 , towards the gap 12 existing between the piston 1 and cylinder 2 , forming a cushion of gas which prevents the contact between the piston 1 and cylinder 2 .
  • At least three restrictors 16 , 17 are necessary in a given section of the cylinder 2 and at least two sections of restrictors 16 , 17 are necessary in the cylinder 2 .
  • the restrictors should be in such opposition that even with the oscillation movement of the piston 1 the restrictors 16 , 17 are never discovered, that is, that the piston 1 does not leave the actuation area of the restrictor 16 , 17 .
  • each restrictor 16 , 17 is regulated, and may also, from a same restrictor 16 , 17 , generate restrictors 16 , 17 with deliberately different flows when such need arises (such as, for example, in the top region of the cylinder 2 ).
  • FIG. 3 illustrates some examples of how to apply the plastic deformation. This can be located in a single point of the restrictor (see FIG. 3 a ), as well as occupying a certain length of the restrictor (see FIG. 3 b ) or even be done along all or almost all the length of the restrictor (see FIG. 3 c ). Such as referred to, the formation of folds (see FIG. 3 d ) may also generate a restriction that decreases the gas flow.
  • the gas flow can be restricted by the most varied means, and the deformation imposed upon the material can be carried out, as shown in FIG. 5 , in a punctual, partial, total manner, with folds, by flattening and by means of any combination thereof.
  • partial deformation there will be at least two different internal sections from each other for the passage of the fluid.
  • the material used is metallic and is of circular section before deformation. In any case, the material may present any section other than circular. These characteristics only depend on the specific needs of each project. Additionally, the material used may be polymer or glass-ceramics.
  • This system may work in closed circuit such that once the specified flow is reached, the system automatically ceases the process of plastic deformation. Accordingly, it is well known that, regardless of the variation of the internal diameter of the restrictor 16 , 17 , restrictors 16 , 17 are obtained with controlled flows, whose variations depend on the accuracy of the system that generates the plastic deformation, as well as the flow measurement system. An example of the process is shown in FIGS. 6 and 7 .
  • FIG. 6 represents the initial stage of the process where the restrictor 16 , 17 is found, with its cross section unaltered, disposed in a system 100 capable of imposing a plastic deformation 100 .
  • a system 100 capable of imposing a plastic deformation 100 is controlled by the flow measurement system 102 .
  • FIG. 7 shows the working of the process at its deformation stage.
  • the restrictor 16 , 17 undergoes a plastic deformation and the gas source under pressure 101 , connected to the restrictor 16 , 17 , sends a gas flow through the restrictor 16 , 17 which is connected to the flow measurement system 102 to take a reading of the flow value of the restrictor 16 , 17 .
  • This value will be compared to a value stipulated previously and, after comparing the results, if the flow value is above that stipulated, a signal is sent to the system that generates the plastic deformation 100 to proceed with the new plastic deformation. This process occurs successively and iteratively until the previously stipulated flow value is achieved. It is therefore guaranteed that said restrictor 16 , 17 , when put to work, provides the necessary gas flow for the correct working of the system.
  • the deformation imposed upon the restrictor 16 , 17 may present an elastic component, causing the occurrence of an elastic return and which, consequently, the gas flow is above that desired, it is possible to carry out the process in more than just a single stage, making it iterative, that is, such that the system makes the chosen deformation and releases the restrictor 16 , 17 letting the deformed region return elastically, during a certain period of time suitable for it to return, then measuring the gas flow. If the flow is still not in accordance with specification, the system causes a new deformation in the restrictor 16 , 17 and then takes a fresh reading and so on and successively until the specified flow value is achieved.
  • This process can be carried out with both metal and polymer materials. Additionally and bearing in mind that the true objective is to guarantee a deformation of the internal section of the material, it is possible to employ a process of deformation by blowing capable of causing a controlled deformation of the restrictor 16 , 17 .
  • glass-ceramic materials deformable by way of a process that feeds the restrictor with heat up to a softening point of the material (glass transition temperature—Tg) which enables its internal section to be molded to a desirable value.
  • Tg glass transition temperature
  • plastic shaping by kneading, constriction, folding, blowing, it is also possible to use a technique of hydroforming or any other that is justifiable. It is further possible, by way of techniques such as hydroforming, to reverse in an absolutely controlled manner, excess deformation imposed upon the restrictor 16 , 17 . This process of plastic shaping also allows the reverse situation to be carried out by deforming it beforehand from inside to out instead of by imposing compressing forces on the material.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Compressor (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Blow-Moulding Or Thermoforming Of Plastics Or The Like (AREA)
  • Shaping Of Tube Ends By Bending Or Straightening (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US14/358,623 2011-11-16 2012-11-14 Restrictor and production process of a fluid leakage restrictor for aerostatic bearings Abandoned US20140318365A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
BRPI1105471A BRPI1105471A2 (pt) 2011-11-16 2011-11-16 restritor e processo de produção de um restritor de vazão de um fluido para mancais aerostáticos
BRPI1105471-9 2011-11-16
PCT/BR2012/000451 WO2013071385A1 (fr) 2011-11-16 2012-11-14 Réducteur et procédé de production d'un réducteur de fuite fluidique pour paliers à air

Publications (1)

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US20140318365A1 true US20140318365A1 (en) 2014-10-30

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US14/358,623 Abandoned US20140318365A1 (en) 2011-11-16 2012-11-14 Restrictor and production process of a fluid leakage restrictor for aerostatic bearings

Country Status (10)

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US (1) US20140318365A1 (fr)
EP (1) EP2780595B1 (fr)
JP (1) JP2015505925A (fr)
KR (1) KR20140091059A (fr)
CN (1) CN104040176A (fr)
BR (1) BRPI1105471A2 (fr)
ES (1) ES2578156T3 (fr)
MX (1) MX2014005836A (fr)
SG (1) SG11201402371YA (fr)
WO (1) WO2013071385A1 (fr)

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US20200064030A1 (en) * 2017-05-17 2020-02-27 Liping NING Double acting alpha stirling refrigerator
US11125272B2 (en) * 2016-04-05 2021-09-21 Fanuc Corporation Throttle unit and a static pressure bearing device equipped with the throttle unit, and a method of manufacturing a grooved block

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BR102013003056A2 (pt) * 2013-02-07 2014-09-16 Whirlpool Sa Restritor de fluxo e compressor de gás
DE102014200981A1 (de) * 2014-01-21 2015-07-23 BSH Hausgeräte GmbH Verdichter für einen Kältekreislauf eines Haushaltskältegeräts, Haushaltskältegerät mit einem Verdichter und Verfahren zum Betreiben eines Verdichters eines Haushaltskältegeräts
CN106089632B (zh) * 2016-07-21 2018-03-02 陕西仙童科技有限公司 一种无油润滑线性压缩机
CN106640971B (zh) * 2017-03-09 2019-06-28 中国工程物理研究院机械制造工艺研究所 一种静压气体止推轴承
CN108223581B (zh) * 2018-03-12 2023-09-05 浙江工业大学 气体静压主轴节流孔孔径调节装置
CN109630402B (zh) * 2019-01-24 2023-10-24 吉林大学 一种自润滑耐磨抽油泵柱塞

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US20160153446A1 (en) * 2013-07-09 2016-06-02 BSH Hausgeräte GmbH Linear compressor for a domestic appliance and domestic refrigeration appliance
US20150226203A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US9322401B2 (en) * 2014-02-10 2016-04-26 General Electric Company Linear compressor
US11125272B2 (en) * 2016-04-05 2021-09-21 Fanuc Corporation Throttle unit and a static pressure bearing device equipped with the throttle unit, and a method of manufacturing a grooved block
US20200064030A1 (en) * 2017-05-17 2020-02-27 Liping NING Double acting alpha stirling refrigerator
US10760826B2 (en) * 2017-05-17 2020-09-01 Liping NING Double acting alpha Stirling refrigerator

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MX2014005836A (es) 2014-06-04
EP2780595A1 (fr) 2014-09-24
SG11201402371YA (en) 2014-08-28
JP2015505925A (ja) 2015-02-26
CN104040176A (zh) 2014-09-10
WO2013071385A1 (fr) 2013-05-23
KR20140091059A (ko) 2014-07-18
BRPI1105471A2 (pt) 2015-11-10
EP2780595B1 (fr) 2016-04-06
WO2013071385A8 (fr) 2014-07-17
ES2578156T3 (es) 2016-07-21

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