EP3115732A1 - Plaque d'échange thermique et échangeur de chaleur de type plaque - Google Patents

Plaque d'échange thermique et échangeur de chaleur de type plaque Download PDF

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Publication number
EP3115732A1
EP3115732A1 EP15758812.0A EP15758812A EP3115732A1 EP 3115732 A1 EP3115732 A1 EP 3115732A1 EP 15758812 A EP15758812 A EP 15758812A EP 3115732 A1 EP3115732 A1 EP 3115732A1
Authority
EP
European Patent Office
Prior art keywords
heat exchange
exchange plate
center channel
plate
inverted
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.)
Withdrawn
Application number
EP15758812.0A
Other languages
German (de)
English (en)
Other versions
EP3115732A4 (fr
Inventor
Lars Persson
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.)
Danfoss Micro Channel Heat Exchanger Jiaxing Co Ltd
Original Assignee
Danfoss Micro Channel Heat Exchanger Jiaxing Co Ltd
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 Danfoss Micro Channel Heat Exchanger Jiaxing Co Ltd filed Critical Danfoss Micro Channel Heat Exchanger Jiaxing Co Ltd
Publication of EP3115732A1 publication Critical patent/EP3115732A1/fr
Publication of EP3115732A4 publication Critical patent/EP3115732A4/fr
Withdrawn legal-status Critical Current

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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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media

Definitions

  • the present invention relates to the fields of heating, ventilation and air conditioning, motor vehicles, cooling and transportation, and in particular relates to a heat exchange plate and a plate-type heat exchanger using the heat exchange plate.
  • plate-type heat exchangers are usually channel structures characterized by an inverted-V shape (fishbone form). Such a structure has good transverse flow priority, and can realize lateral flow distribution very well, and so has a good heat exchange effect.
  • inverted-V-shaped structures is relatively inflexible, and offers little room for improvement in terms of significantly enhancing heat exchange and increasing strength (in order to reduce material thickness).
  • the corrugation width and assembly result of an inverted-V-shaped structure determine the welding space per unit area, and therefore the strength is limited.
  • the way in which channels between inverted-V-shaped plates intersect and the density of welding points thereof determine the intensity of turbulence arising when fluid passes these positions. Under restricted parameter variation conditions, the intensity of turbulence is limited, so there is no way of achieving a greater heat exchange enhancement effect.
  • the object of the present invention is to resolve at least one aspect of the abovementioned problems and shortcomings in the prior art.
  • a heat exchange plate is provided, at least one surface of each heat exchange plate comprising ridges and grooves which are arranged alternately.
  • Multiple fluid distribution adjustment structures are disposed on crests of the ridges and/or trough bottoms of the grooves.
  • each of the fluid distribution adjustment structures comprises protrusions on two edges respectively of the crest or trough bottom, and a center channel between the two edges.
  • the protrusion comprises any one of a cylinder, a cuboid with rounded corners, a trapezoidal structural body and an arcuate protrusion, or any combination thereof;
  • the center channel comprises a flat, straight channel and/or a channel formed by a multi-element curved-surfaced structural body.
  • a smooth connection structure is disposed between the protrusion and the heat exchange plate surface, and the multi-element curved-surfaced structural body comprises a combination of curved arc/multi-element curved line/multi-element arc and straight line/curved line/arc multi-element bodies.
  • the base of the center channel is substantially flush with or depressed relative to the crest or trough bottom.
  • a part between the two protrusions on each edge forms an inlet or outlet of the center channel.
  • the protrusions are disposed at intervals on the front edge and/or rear edge of the crest or trough bottom.
  • the protrusions on the front edge are staggered with respect to the protrusions on the rear edge in a horizontal direction perpendicular to a direction of extension of the center channel.
  • the center channel is curved in the direction of extension of the crest or trough bottom.
  • at least a portion of the protrusions are set to at least partially cover the center channel so as to form an intermittent center channel.
  • a part or all of the surface is provided with a structural pattern with a single half-inverted-V-shape and/or inverted-V-shape, or a double half-inverted-V-shape and/or inverted-V-shape, or a greater number of repetitions of a half-inverted-V-shape and/or inverted-V-shape, and each heat exchange plate comprises a fluid inlet and a fluid outlet located at two opposite ends respectively in a direction of extension of the heat exchange plate.
  • a plate-type heat exchanger comprises the heat exchange plate described above.
  • the inventive concept of the present invention lies in providing various protrusion structures, curved structures or depressed structures on flat edges of ridges and/or grooves in an inverted-V-shaped or fishbone heat exchange plate in the prior art.
  • Such an arrangement enables the heat exchange plate to generate more turbulence, and increases heat transfer while maintaining consistent fluid distribution.
  • the strength of fluid channels in the heat exchange plate is enhanced, and this is beneficial for reducing the thickness of the heat exchange plate.
  • Figs. 1 and 2 show a view of the overall structure of a heat exchange plate in the plate-type heat exchanger of the present invention and a corresponding sectional view.
  • the plate-type heat exchanger comprises multiple A-shaped heat exchange plates and V-shaped heat exchange plates (referred to as a pair of heat exchange plates below for convenience of description), which are stacked together between an end plate and a base plate.
  • the heat exchange plates may also be a combination of W-shaped and M-shaped heat exchange plates; this is common knowledge in the art, and is not described in detail again here. All that is required is for the multiple combined heat exchange plates to be capable of forming a manifold for the passage of fluid.
  • a surface of the heat exchange plate may be provided with a pattern structure with a single inverted-V-shape (A/V shape), a pattern structure with a double inverted-V-shape (M/W shape) or a pattern structure with a greater number of repetitions of an inverted-V-shape.
  • the pattern feature on the heat exchange plate may also be a single half-inverted-V-shape or a greater number of repetitions thereof.
  • Fig. 1 shows that the heat exchange plate 10 is a heat exchange plate having an inverted-V-shaped (or fishbone) pattern structure. That is, multiple ridges 1 and grooves 2 are arranged alternately in the longitudinal direction of the heat exchange plate 10. The trough bottoms of the grooves 2 are indicated by the dotted lines in Fig. 1 .
  • Those skilled in the art will appreciate that such a structural arrangement is a typical design for an existing inverted-V-shaped heat exchange plate pattern.
  • parameters such as the widths of the ridges 1 and grooves 2, and the height of the ridges 1 and the depth of the grooves 2 may be designed as required.
  • Fig. 1 shows that the heat exchange plate 10 is a heat exchange plate having an inverted-V-shaped (or fishbone) pattern structure. That is, multiple ridges 1 and grooves 2 are arranged alternately in the longitudinal direction of the heat exchange plate 10. The trough bottoms of the grooves 2 are indicated by the dotted lines in Fig. 1 .
  • the ridges 1 and the grooves 2 have flat crests and trough bottoms, 3 and 4, respectively, with the widths thereof being indicated by the labels w1 and w2 respectively.
  • the widths w1 and w2 may be set to be the same or different.
  • the width w1 of the flat crest 3 of the ridge 1 is greater than the width w2 of the flat trough bottom 4 of the groove 2.
  • the widths of the flat crests 3 of the ridges 1 are all set to be the same, and correspondingly, the widths of the flat trough bottoms 4 of the grooves 2 are set to be the same as each other.
  • those skilled in the art could set the abovementioned structural parameters as required.
  • the scenario described above is merely an example, which must not be interpreted as a limitation of the present invention.
  • Figs. 3a - 3c show, in order to generate greater turbulence and enhance the strength of fluid channels on the heat exchange plate 10, multiple fluid distribution adjustment structures are added to the flat crests 3 of the ridges 1 in the present invention. Furthermore, it is also possible to add multiple fluid distribution adjustment structures on the trough bottoms 4.
  • the fluid distribution adjustment structure may comprise any one of a cylinder, a cuboid with rounded corners, a trapezoidal structural body and an arcuate protrusion, or any combination thereof.
  • the fluid distribution adjustment structure is only provided on the crests 3 of the ridges 1 of the heat exchange plate 10, but those skilled in the art will understand, based on the disclosed content of the present invention, that the fluid distribution adjustment structure could likewise be provided on the trough bottoms 4 of the grooves 2 in a similar way. That is, those skilled in the art could choose to provide the fluid distribution adjustment structure on the crests 3 of the ridges 1 and/or on the trough bottoms 4 of the grooves 2 as required, with no need to be restricted to the case shown in the figures of the present invention.
  • one ridge 1 and one groove 2 which are adjacent to each other are defined here as one flow unit.
  • two edges of the crest 3 of the ridge 1 are defined as or referred to as a front edge 31 and a rear edge 32.
  • Multiple flow distribution adjustment structures 5 are disposed at intervals of a predetermined distance along the front edge 31 and/or the rear edge 32.
  • the main function of the fluid distribution adjustment structure 5 is to further adjust and distribute fluid, and therefore any structural arrangement, such as a cylinder, a cuboid with rounded corners, a trapezoidal structural body or an arcuate protrusion, could be used as the fluid distribution adjustment structure referred to here, which is not restricted to any particular form.
  • any structural arrangement such as a cylinder, a cuboid with rounded corners, a trapezoidal structural body or an arcuate protrusion, could be used as the fluid distribution adjustment structure referred to here, which is not restricted to any particular form.
  • small cylinders and a middle gap therebetween are used as the fluid distribution adjustment structure 5.
  • the cylinders 51 may be disposed at equal intervals along the front edge 31 or rear edge 32, with the cylinders 51 on the front edge 31 and rear edge 32 being arranged in alignment or in one-to-one correspondence with one another in a direction perpendicular to the direction of extension of the front edge 31 or rear edge 32, but this is of course not necessary.
  • the cylinders 51 are located at the front edge 31 and rear edge 32 respectively.
  • a center channel 6 between the cylinders 51 is also provided on the crest 3.
  • the fluid distribution adjustment structure 5 comprises protrusions (e.g. cylinders 51) at the front edge 31 and rear edge 32 of the crest 3 of each ridge 1, and the center channel 6 between two protrusions.
  • the protrusions are not limited to structural bodies of regular shape such as cylinders, pits, cuboids with rounded corners and trapezoidal structural bodies, but may also be structural bodies of irregular shape such as ellipses and pointed tips.
  • the center channel 6 comprises a flat, straight channel and/or a channel formed by a multi-element curved-surfaced structural body. In this example, for the purpose of explanation, the center channel is set to be substantially V-shaped.
  • cylinders or small cylinders 51 are disposed at intervals along the front edge 31 or rear edge 32.
  • a substantially light-impermeable cross section is obtained in the length direction of the heat exchange plate 10, as shown in Fig. 3c for example.
  • Such a light-impermeable or quasi-light-impermeable cross section characteristic is very important for the evaporation process. Gaseous coolant in a two-phase coolant flowing in through a fluid inlet of the heat exchange plate 10 will flow away through the sides, to trigger the process of "boiling" of liquid coolant.
  • the small center channel 6 is located between two cylinders 51, i.e.
  • the center channel 6 may be used to evaporate liquid coolant.
  • the depth used for the center channel 6 is very small, and the boundary layer or liquid film thickness of liquid coolant is quite small; this is conducive to enhancement of the boiling process.
  • coolant passes through the above-mentioned region, there is significant turbulence. This is also conducive to enhancement of the boiling process.
  • the center channel 6 is generally formed of a multi-element curved-surfaced structural body which comprises a combination of curved arc/multi-element curved line/multi-element arc and straight line/curved line/arc multi-element bodies.
  • the center channel 6 is generally set to have a curved surface structure which transitions smoothly.
  • the center channel 6 may be set to have a depressed V-shape relative to the crest 3 as shown in Fig. 3 , but multiple protrusions are provided on the two opposite edges 31 and 32 of the crest 3, and therefore even if the center channel 6 were set to be substantially flush with the crest, the middle part or gap disposed between the opposite edges 31 and 32 would still be able to serve the function of a center channel.
  • FIG. 4 shows, an open space between two adjacent cylinders 51 on the front edge 31 or rear edge 32 is an inlet 71 and outlet 72 of the flow unit formed by one ridge 1 and one groove 2 which are adjacent to each other.
  • the arrow shows the flow direction of fluid; the inlets 71 and outlets 72 on the front edge 31 and rear edge 32 are used to break up liquid coolant into small droplets. This is conducive to evaporation of coolant. Furthermore, the turbulence achieved here also enhances heat transfer.
  • the center channel 6 may be used to homogenize fluid distribution, and reduce the thickness of the coolant boundary layer and liquid film.
  • Fig. 5 shows another variation of the center channel according to the present invention.
  • the center channel 6 is set to extend in a flat and straight manner, substantially parallel to the front edge 31 and/or rear edge 32 of the ridge 1.
  • the variation shown in Fig. 5 differs therefrom in that the center channel 6' is set to be curved along the front edge 31 and/or rear edge 32.
  • the center channel 6' is set to have a curved form along the front edge 31 and/or rear edge 32; of course, the center channel 6' could also be set to be curved in a direction different from the abovementioned direction, or to be curved in any form.
  • Such an arrangement will make the process of coolant flow smoother.
  • more active heat transfer regions i.e. heat transfer areas
  • more turbulence is generated to enhance the boiling process.
  • Fig. 6 shows the intermittent layout of inlets and outlets.
  • small cylinders 51 with the same structure are no longer disposed at intervals along the front edge 31 and/or rear edge 32; instead, small cylinders 51 and larger structural bodies (in this example, cuboids with chamfered or rounded corners) 81 are arranged alternately at predetermined intervals along the front edge 31 and/or rear edge 32.
  • the flow cross section of the basic flow unit is reduced, and the flow speed of fluid such as coolant will increase.
  • more turbulence will be generated.
  • top regions on the two edges front edge 31 and rear edge 32
  • the arrow shows the flow direction of fluid, such as coolant.
  • Fig. 7 shows an example in which the crest of the ridge has an intermittent center channel.
  • Fig. 4 shows that the center channel 6 is continuous, the center channel 6 may also be set to have an intermittently blocked form.
  • the interval between small cylinders 51 disposed along the front edge 31 and rear edge 32 has been expanded, in order to accommodate, between two small cylinders 51 which are adjacent in the direction of extension of the front edge 31 and/or rear edge 32, a structural body 82 which is larger than the small cylinder.
  • the structural body 82 is dimensioned so as to keep spaced apart the small cylinders 51 adjacent thereto on the front edge 31 and/or rear edge 32, and at the same time partially or completely block the center channel 6.
  • FIG. 7 shows the case in which an ellipsoid, elongated rounded body or cuboid with rounded corners 82 completely blocks the center channel 6 in a direction perpendicular to the front edge 31 or rear edge 32, wherein the cuboid 82 is spaced apart from four adjacent small cylinders 51.
  • Figs. 8a and 8b show, respectively, an overall view of the heat exchange plate 10 according to another embodiment of the present invention, and the main features in the optimized technical solution in Fig. 8a .
  • the heat exchange plate 10 comprises ports 11, 12, 13 and 14 for fluid. It can be understood that those skilled in the art could select suitable ports 11, 12, 13 and 14, as required, for fluid to flow in and flow out.
  • Fig. 8b shows an enlarged view of a middle part of the heat exchange plate 10 in Fig. 8a . It can be seen from the enlarged view that ridges 1 and grooves 2 are disposed alternately from left to right, with multiple fluid distribution adjustment structures 5 being disposed at intervals (in a direction from bottom to top) on the front edges 31 and rear edges 32 of the ridges 1. Since the fluid distribution adjustment structure 5 is set to be a curved or winding structure as shown in the figure (e.g. substantially in the shape of a double hook), a curved center channel 6' is formed in a part between the front edge 31 and rear edge 32.
  • the structures shown in Figs. 8a and 8b reflect a notable advantage of the present invention in terms of the design of the ratio of groove width to ridge width. That is, by adjusting the width ratio relationship between the ridges and grooves, and the dimensions of the corresponding fluid adjustment structures, it is very easy to obtain a heat exchange plate with a high degree of asymmetry.
  • a heat exchange plate with a high degree of asymmetry.
  • the present invention will provide a better evaporation result, and provide a user with a higher evaporation temperature under the same conditions; on the other hand, the present invention also effectively reduces the channel pressure drop on the water side (auxiliary side), thereby increasing the energy efficiency of the water pump in the user unit system.
  • a plate design pattern of a substantially W-shaped and M-shaped pattern may also be used for the present invention.
  • a two-phase coolant flows into fluid channels on the heat exchange plates.
  • the coolant encounters a net gap (such as the groove 2 shown in Fig. 1 )
  • the coolant will preferably flow away from the sides.
  • the entire V/A(M/W)-shaped center channel will be filled. This is beneficial for fluid distribution.
  • Coolant will then enter through the inlets 71 on the front edge 31 of the ridge 1.
  • the small entry space will control the liquid coolant to uniformly distribute them.
  • the semi-closed cross-sectional space will force vapor of gaseous coolant to flow in a curved, winding manner, for the purpose of preventing bypass flow.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP15758812.0A 2014-03-04 2015-02-13 Plaque d'échange thermique et échangeur de chaleur de type plaque Withdrawn EP3115732A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201410076347.4A CN103822521B (zh) 2014-03-04 2014-03-04 换热板及板式换热器
PCT/CN2015/073025 WO2015131759A1 (fr) 2014-03-04 2015-02-13 Plaque d'échange thermique et échangeur de chaleur de type plaque

Publications (2)

Publication Number Publication Date
EP3115732A1 true EP3115732A1 (fr) 2017-01-11
EP3115732A4 EP3115732A4 (fr) 2017-12-27

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP15758812.0A Withdrawn EP3115732A4 (fr) 2014-03-04 2015-02-13 Plaque d'échange thermique et échangeur de chaleur de type plaque

Country Status (3)

Country Link
EP (1) EP3115732A4 (fr)
CN (1) CN103822521B (fr)
WO (1) WO2015131759A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10989482B2 (en) 2017-01-19 2021-04-27 Alfa Laval Corporate Ab Heat exchanging plate and heat exchanger

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103822521B (zh) * 2014-03-04 2017-02-08 丹佛斯微通道换热器（嘉兴）有限公司 换热板及板式换热器
CN110095007A (zh) * 2019-05-28 2019-08-06 西安热工研究院有限公司 一种紧凑式换热器
CN114909929A (zh) * 2021-02-08 2022-08-16 浙江三花汽车零部件有限公司 换热器

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US3372743A (en) * 1967-01-25 1968-03-12 Pall Corp Heat exchanger
SE353954B (fr) * 1971-02-19 1973-02-19 Alfa Laval Ab
ATA166091A (de) * 1991-08-23 1996-02-15 Faigle Heinz Kg Füllkörper
JP3094979B2 (ja) * 1997-12-10 2000-10-03 ダイキン工業株式会社 プレート式熱交換器
JP2000283682A (ja) * 1999-03-31 2000-10-13 Hisaka Works Ltd プレート式熱交換器
CN2415336Y (zh) * 2000-04-17 2001-01-17 刘澄清 换热器
ES2279267T5 (es) * 2004-08-28 2014-06-11 Swep International Ab Un intercambiador de calor de placas
FR2876179B1 (fr) * 2004-10-04 2007-02-16 Alfa Laval Vicarb Sa Echangeur de chaleur a plaques specifiques
DE202007007169U1 (de) * 2007-05-16 2008-09-25 Akg-Thermotechnik Gmbh & Co. Kg Wärmeaustauscher für gasförmige Medien
CN101158561A (zh) * 2007-11-26 2008-04-09 北京市京海换热设备制造有限责任公司 板式换热器复合波纹板束
JP5191066B2 (ja) * 2008-07-10 2013-04-24 コリア デルファイ オートモーティブ システムズ コーポレーション 変速機オイルクーラー
KR100950689B1 (ko) * 2009-04-16 2010-03-31 한국델파이주식회사 플레이트 열교환기
CN103822521B (zh) * 2014-03-04 2017-02-08 丹佛斯微通道换热器（嘉兴）有限公司 换热板及板式换热器

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10989482B2 (en) 2017-01-19 2021-04-27 Alfa Laval Corporate Ab Heat exchanging plate and heat exchanger

Also Published As

Publication number Publication date
CN103822521B (zh) 2017-02-08
EP3115732A4 (fr) 2017-12-27
WO2015131759A1 (fr) 2015-09-11
CN103822521A (zh) 2014-05-28

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