US20160146215A1 - Centrifugal rotor - Google Patents

Centrifugal rotor Download PDF

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Publication number
US20160146215A1
US20160146215A1 US14/898,239 US201414898239A US2016146215A1 US 20160146215 A1 US20160146215 A1 US 20160146215A1 US 201414898239 A US201414898239 A US 201414898239A US 2016146215 A1 US2016146215 A1 US 2016146215A1
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US
United States
Prior art keywords
flange
centrifugal rotor
rotor
centrifugal
longitudinal axis
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.)
Abandoned
Application number
US14/898,239
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English (en)
Inventor
Stéphane Sgambati
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.)
Linde GmbH
Cryostar SAS
Original Assignee
Linde GmbH
Cryostar 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 Linde GmbH, Cryostar SAS filed Critical Linde GmbH
Assigned to LINDE AKTIENGESELLSCHAFT reassignment LINDE AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: Sgambati, Stéphane
Assigned to CRYOSTAR SAS reassignment CRYOSTAR SAS ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: Sgambati, Stéphane
Publication of US20160146215A1 publication Critical patent/US20160146215A1/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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2272—Rotors specially for centrifugal pumps with special measures for influencing flow or boundary layer
    • 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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • 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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes

Definitions

  • the present invention relates to a centrifugal rotor.
  • the technical field of this invention is that of the fluid, liquid or gaseous compression.
  • the invention therefore relates to both pumps as well as compressors which make a supply of liquid or gas respectively possible, from a given pressure to a higher pressure.
  • a centrifugal rotor is a rotor having an axis of rotation. It is designed to compress a fluid flowing in a direction parallel to its axis of rotation, the compressed fluid leaving the rotor in a radial direction outwardly.
  • the element used for this purpose is a fixed part called an axial diffuser and it has at least one duct to direct the compressed fluid.
  • the downstream end of the duct that is to say the end which is remote from the centrifugal rotor, is axially oriented in accordance with the direction that one wishes to direct the compressed fluid.
  • the purpose of the axial diffuser is to then take a turn at about 90° to the outgoing fluid from the centrifugal rotor so as to guide it axially.
  • Document FR-2874241 discloses a high-efficiency centrifugal rotor which uses truncated blades with a radial diffuser. The wake of the blade recloses in the diffuser and by working with the wakes of the other adjacent blades creates a stratified flow that gradually expands within the diffuser. We thus find in this document a rotor incorporating a diffuser. The very thick blades are located in the lower part of the rotor.
  • U.S. Pat. No. 1,447,916 illustrates another embodiment of a rotor incorporating a diffuser.
  • the latter may be a single piece with the rotor portion comprising blades or it may be a separate piece secured to the rotor portion comprising the blades.
  • An object of this invention is thus, for a given compression stage, comprising a centrifugal rotor and an axial diffuser, to increase the performance of this stage, i.e., for example, obtaining a higher compression ratio for a given power or for a given compression reducing the mechanical power needed to be exerted on the rotor to make it turn.
  • this invention proposes a centrifugal rotor including:
  • a hub having a longitudinal axis
  • a second flange separated downstream from said first flange by the vanes thereby forming channels each delimited by the first flange, the second flange and two vanes extending from the fluid inlet to a peripheral outlet.
  • the first flange in the proximity of the peripheral outlet, has a concave area oriented towards the channels while the second flange has a convex area oriented towards the channels.
  • the first flange and the second flange advantageously have a circular shape around the longitudinal axis.
  • the surface tangent to the concave region of the first flange exiting the channel forms an angle of between 1° and 45°, preferably between 10° and 30°, with a radial plane perpendicular to the longitudinal axis.
  • the surface tangent to the convex region of the second flange exiting the channel forms an angle of between 1° and 45°, preferably between 10° and 30°, with a radial plane perpendicular to the longitudinal axis.
  • the vanes extend to the outer peripheral exterior edge of the first flange and/or of the second flange.
  • the first flange advantageously has an outer peripheral edge adjacent to the channels which have a greater diameter than an outer peripheral edge adjacent to the channels of the second flange.
  • the speed is therefore higher. This is preferable because the path to be traveled along the outside of a turn is greater than that of the inside of a turn. In this way, a more uniform distribution of the velocity is promoted when the fluid then moves in a substantially longitudinal direction.
  • This invention further relates to a centrifugal compressor and/or a centrifugal pump comprising a centrifugal rotor as described above.
  • FIG. 1 illustrates a centrifugal rotor of the prior art with a cross sectional view of a half rotor mounted in a compressor
  • FIG. 2 is a view similar to that of FIG. 1 for a centrifugal rotor according to a first embodiment of this invention
  • FIG. 3 is a view similar to the preceding views according to a second embodiment of this invention.
  • FIG. 4 is a cross-section view in perspective along the cut line IV-IV of FIG. 2 .
  • centrifugal rotor 2 in FIG. 1 mounted inside a housing 4 , for example a compressor housing, and a shaft 6 having a longitudinal axis 8 .
  • a working air compressor or more generally a gaseous fluid compressor
  • this invention may also be applied to pumps for liquids.
  • the air (or other gaseous fluid) is drawn into the centrifugal rotor 2 in a longitudinal direction relative to the longitudinal axis 8 , and is driven in a mixed flow motion in the centrifugal rotor 2 while rotating and appear radially with respect to the longitudinal axis 8 .
  • the centrifugal rotor 2 is built in one piece and comprises a hub 10 , a first flange or upstream flange 12 , a second flange or downstream flange 14 and vanes 16 .
  • the hub 10 enables a connection between the shaft 6 and the centrifugal rotor 2 . It has an overall circular, cylindrical, tubular shape and is provided with a means to fasten it to the shaft 6 .
  • a longitudinal groove is typically provided in the hub 10 and the shaft 6 to receive a longitudinal spline or even grooves, or any other type of connection.
  • the downstream flange 14 is connected directly to the hub 10 and extends radially relative to the longitudinal axis 8 .
  • the upstream/downstream direction is defined relative to the direction of the air flow in the centrifugal rotor 2 . Indeed, in FIG. 1 (as well as in the other figures) air is drawn to the right of the rotor and then moves longitudinally to the left before being driven in a radial direction to be oriented finally, after leaving the centrifugal rotor 2 in a longitudinal direction back towards the left of the figure.
  • the upstream elements are arranged to the right of the downstream elements in the figures.
  • the upstream flange 12 faces the downstream flange 14 and is connected thereto by the vanes 16 thereby defining the channels for the air between the two flanges.
  • the air is thus introduced between the inner surfaces of the flanges and vanes in a centrifugal radial manner.
  • the upstream flange 12 does not extend to the hub 10 but remains at a distance therefrom.
  • a sealing bearing 18 faces the hub 10 in front.
  • the front sealing bearing 18 with the hub 10 defines an inlet chamber 20 with an annular opening 22 upstream of the inlet chamber 20 .
  • the front sealing bearing 18 is machined to enable it to create a seal of the centrifugal rotor 2 in rotation within the housing 4 .
  • a seal may be used, such as for example a labyrinth ring 24 , as an interface between the centrifugal rotor 2 and the housing 4 .
  • the centrifugal rotor 2 also includes a further sealing bearing 18 on the downstream side, or a rear sealing bearing, which extends from the downstream flange 14 and receives another labyrinth ring 24 .
  • the channels driving air between the upstream flange 12 and downstream flange 14 each have an outlet 26 ( FIG. 1 ) radially oriented at the largest diameter of the flanges.
  • the air then enters a diffuser 28 in which it is guided so that the air flow is more longitudinal than radial.
  • the channels 30 in the diffuser 28 also make it possible to convert the helical movement of the air flow to a substantially straight movement.
  • FIGS. 2 and 4 illustrate a first embodiment of a centrifugal rotor according to this invention.
  • the overall structure is substantially the same in FIG. 1 and in FIGS. 2 to 4 .
  • the references in FIG. 1 are used in FIGS. 2 to 4 to designate similar elements.
  • a centrifugal rotor is thus found 2 rotatably mounted in a housing 4 around a shaft 6 having a longitudinal axis 8 .
  • the centrifugal rotor 2 is sealed off relative to the housing 4 thusly ensured in particular through the sealing bearings 18 working together with the labyrinth rings 24 (or other type of seal).
  • a hub 10 enables a connection between the rotor and the shaft 6 , for example by means of a spline that is not shown.
  • the centrifugal rotor 2 further comprises an upstream flange 12 and downstream flange 14 interconnected by vanes 16 .
  • the upstream flange 12 has a sealing bearing 18 which with the hub 10 defines an inlet chamber 20 of the annular opening 22 .
  • this invention proposes to provide an outlet for air flow in a centrifugal rotor (or other fluid) having an improved velocity vector to enter into the longitudinal diffuser.
  • a centrifugal rotor or other fluid
  • the air channels will be slightly bent (defined by the flanges and the vanes) in the centrifugal rotor 2 close to the outlets 26 .
  • a curvature is thus produced at the output of the centrifugal rotor which makes it possible to increase the speed of the air towards the outside of the curvature.
  • the inner face of the upstream flange 12 and the surface of the downstream flange 14 are substantially plane (and slightly converging), the inner surface of the upstream flange 12 has, near the output 26 , a concave area 32 and the inner surface of the downstream flange 14 has, near the outlet 26 , opposite the concave area 32 , a convex area 34 .
  • this surface is substantially conical (cone axis of the longitudinal axis 8 ) and forms, with a radial plane illustrated by a dotted line, angle a.
  • this angle is about 15° and it is about 30° in the embodiment of FIG. 3 .
  • this angle will be comprised between 10° and 45°. In the centrifugal rotors of the prior art, as illustrated by FIG. 1 , this angle is substantially zero.
  • the surface tangent to the inner surface of the upstream flange 12 was not illustrated.
  • a substantially conical surface is also found here, around the longitudinal axis 8 , which forms, with the radial plane illustrated, an angle which is preferably less than 45°, for example between 10 and 45°.
  • FIG. 4 illustrates that the vanes 16 extend into the convex area 34 of the downstream flange 14 . Of course, they extend in a similar manner into the concave zone 32 of the upstream flange 12 . Preferably, as illustrated in this FIG. 4 , the vanes 16 extend to the peripheral edge of the upstream flange 12 and the downstream flange 14 , that is to say, up to the output 26 of the rotor.
  • H is referenced by the line having the greatest diameter of the inner surface of the downstream flange 14 and by S for the line having the greatest diameter of the inner surface of the upstream flange 12 .
  • S and H are circles the center of which lies on the longitudinal axis 8 .
  • R S and R H radius respectively.
  • R S >R H the peripheral speed of the air in the vicinity of point S is greater than that of the air near the point H. This also applies to the absolute tangential velocity.
  • the air is accelerated from the upstream side (exterior to the exiting “turn” of the rotor), thereby making it possible to have a more uniform speed at the input of a substantially longitudinal section of the diffuser. Therefore, the losses in pressure, if only within the diffuser, are reduced and therefore make it possible to increase the yield of the device.
  • the shape of the centrifugal rotor according to this invention thus allows a more gradual transition from a radial air flow to a longitudinal flow.
  • the distribution of fluid velocities through a passage section of the diffuser is more uniform and regular.
  • the pressure drops are thus limited and again in terms of yield is obtained at a time when the fluid passes from an essentially radial flow to an axial flow as it flows into the axial diffuser.
  • the channels in the centrifugal rotor 2 have a passage in which the flow is substantially radial.
  • the inner surfaces of the upstream flange and the downstream flange each have an inversion of curvature.
  • the inner surface of the upstream flange 12 has a convex area near the inlet chamber 20 and then it extends from the hub 10 after a curved area, said inner surface has a concave area as described above.
  • the inner surface of the upstream flange 14 has a convex area near the inlet chamber 20 and then it extends from the hub 10 after a curved area, said inner surface has a concave area as described above.
  • the trajectory of the fluid in the channels defined by the flanges and the vanes in the centrifugal rotor 2 and thus has a curve.
  • the vanes 16 extend into the curved region (that is to say up to the concave area of the inner surface of the upstream flange and to the convex area of the inner surface of the downstream flange) and guide the fluid preferably to the outlet 26 .
  • the blades 16 thus are also curved. They preferably extend from the inlet chamber 20 to the line H and the line S. or for example up to the vicinity of these lines (to least 10 mm in these lines).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US14/898,239 2013-06-18 2014-06-18 Centrifugal rotor Abandoned US20160146215A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR1355696 2013-06-18
FR1355696A FR3007086B1 (fr) 2013-06-18 2013-06-18 Roue centrifuge
PCT/FR2014/051512 WO2014202903A1 (fr) 2013-06-18 2014-06-18 Roue centrifuge

Publications (1)

Publication Number Publication Date
US20160146215A1 true US20160146215A1 (en) 2016-05-26

Family

ID=48980150

Family Applications (1)

Application Number Title Priority Date Filing Date
US14/898,239 Abandoned US20160146215A1 (en) 2013-06-18 2014-06-18 Centrifugal rotor

Country Status (9)

Country Link
US (1) US20160146215A1 (enrdf_load_stackoverflow)
EP (1) EP3011185B1 (enrdf_load_stackoverflow)
JP (1) JP2016522357A (enrdf_load_stackoverflow)
KR (1) KR20160021229A (enrdf_load_stackoverflow)
CN (1) CN105518307A (enrdf_load_stackoverflow)
CA (1) CA2915720C (enrdf_load_stackoverflow)
FR (1) FR3007086B1 (enrdf_load_stackoverflow)
RU (1) RU2015154050A (enrdf_load_stackoverflow)
WO (1) WO2014202903A1 (enrdf_load_stackoverflow)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120036865A1 (en) * 2009-04-06 2012-02-16 Turbomeca Air bleed having an inertial filter in the tandem rotor of a compressor
US20150118061A1 (en) * 2013-10-31 2015-04-30 André Hildebrandt Radial Compressor
US20150118037A1 (en) * 2013-10-28 2015-04-30 Minebea Co., Ltd. Centrifugal fan
CN113302401A (zh) * 2019-01-21 2021-08-24 三菱电机株式会社 送风机、室内机以及空调机
US20240060499A1 (en) * 2022-08-22 2024-02-22 Hamilton Sundstrand Corporation Rotor integrated axial flux electric motor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10533568B2 (en) * 2017-10-30 2020-01-14 Daikin Applied Americas Inc. Centrifugal compressor with seal bearing

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GB636290A (en) * 1947-01-09 1950-04-26 Lysholm Alf Improvements in diffusers for centrifugal compressors
US2543923A (en) * 1948-04-13 1951-03-06 Ward T Mixsell Radial air compressor
US3850550A (en) * 1971-08-05 1974-11-26 Hydr O Matic Pump Co Centrifugal pump and motor
US4219306A (en) * 1978-03-07 1980-08-26 Kawasaki Jukogyo Kabushiki Kaisha Multistage turbocompressor with multiple shafts
US5634772A (en) * 1993-10-21 1997-06-03 Ebara Corporation System for controlling operation of turbo type fluid machinery
US20020119038A1 (en) * 2001-02-23 2002-08-29 Abdallah Shaaban A. Fluid flow controller
RU2197644C1 (ru) * 2001-07-30 2003-01-27 Открытое акционерное общество "Татнефть" Рабочее колесо центробежного насоса
US20120051933A1 (en) * 2010-08-31 2012-03-01 Douglas Carl Hofer Supersonic compressor rotor and method of assembling same
US20140127023A1 (en) * 2011-05-23 2014-05-08 Turbomeca Centrifugal compressor impeller

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FR2874241A1 (fr) * 2004-08-16 2006-02-17 Max Sardou Roue centrifuge a haut rendement
JP2006289045A (ja) * 2005-04-14 2006-10-26 Masayoshi Furuichi モーターフアン
JP4502057B2 (ja) * 2008-09-29 2010-07-14 ダイキン工業株式会社 床置型空気調和機の室内機
GB2467968B (en) * 2009-02-24 2015-04-22 Dyson Technology Ltd Centrifugal compressor with a diffuser
JP2013072360A (ja) * 2011-09-28 2013-04-22 Panasonic Corp 電動送風機および電気掃除機

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Publication number Priority date Publication date Assignee Title
US1447916A (en) * 1920-12-18 1923-03-06 American Blower Co Centrifugal fan
GB636290A (en) * 1947-01-09 1950-04-26 Lysholm Alf Improvements in diffusers for centrifugal compressors
US2543923A (en) * 1948-04-13 1951-03-06 Ward T Mixsell Radial air compressor
US3850550A (en) * 1971-08-05 1974-11-26 Hydr O Matic Pump Co Centrifugal pump and motor
US4219306A (en) * 1978-03-07 1980-08-26 Kawasaki Jukogyo Kabushiki Kaisha Multistage turbocompressor with multiple shafts
US4219306B1 (enrdf_load_stackoverflow) * 1978-03-07 1992-07-21 Fujino Yoshikazu
US5634772A (en) * 1993-10-21 1997-06-03 Ebara Corporation System for controlling operation of turbo type fluid machinery
US20020119038A1 (en) * 2001-02-23 2002-08-29 Abdallah Shaaban A. Fluid flow controller
RU2197644C1 (ru) * 2001-07-30 2003-01-27 Открытое акционерное общество "Татнефть" Рабочее колесо центробежного насоса
US20120051933A1 (en) * 2010-08-31 2012-03-01 Douglas Carl Hofer Supersonic compressor rotor and method of assembling same
US20140127023A1 (en) * 2011-05-23 2014-05-08 Turbomeca Centrifugal compressor impeller

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120036865A1 (en) * 2009-04-06 2012-02-16 Turbomeca Air bleed having an inertial filter in the tandem rotor of a compressor
US9611862B2 (en) * 2009-04-06 2017-04-04 Turbomeca Air bleed having an inertial filter in the tandem rotor of a compressor
US20150118037A1 (en) * 2013-10-28 2015-04-30 Minebea Co., Ltd. Centrifugal fan
US20150118061A1 (en) * 2013-10-31 2015-04-30 André Hildebrandt Radial Compressor
US9976566B2 (en) * 2013-10-31 2018-05-22 Man Diesel & Turbo Se Radial compressor
CN113302401A (zh) * 2019-01-21 2021-08-24 三菱电机株式会社 送风机、室内机以及空调机
EP3916238A4 (en) * 2019-01-21 2022-01-19 Mitsubishi Electric Corporation BLOWER FAN, INDOOR UNIT, AND AIR CONDITIONER
US20240060499A1 (en) * 2022-08-22 2024-02-22 Hamilton Sundstrand Corporation Rotor integrated axial flux electric motor

Also Published As

Publication number Publication date
CA2915720C (en) 2021-09-07
JP2016522357A (ja) 2016-07-28
FR3007086A1 (fr) 2014-12-19
EP3011185B1 (fr) 2020-11-04
KR20160021229A (ko) 2016-02-24
WO2014202903A1 (fr) 2014-12-24
RU2019113490A (ru) 2019-06-04
EP3011185A1 (fr) 2016-04-27
RU2019113490A3 (enrdf_load_stackoverflow) 2022-01-14
RU2015154050A (ru) 2017-07-19
CN105518307A (zh) 2016-04-20
CA2915720A1 (en) 2014-12-24
FR3007086B1 (fr) 2015-07-03

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