EP3150855B1 - Offener verdichter - Google Patents

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Publication number
EP3150855B1
EP3150855B1 EP15829255.7A EP15829255A EP3150855B1 EP 3150855 B1 EP3150855 B1 EP 3150855B1 EP 15829255 A EP15829255 A EP 15829255A EP 3150855 B1 EP3150855 B1 EP 3150855B1
Authority
EP
European Patent Office
Prior art keywords
oil supply
supply passage
axial
drive shaft
passage
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
EP15829255.7A
Other languages
English (en)
French (fr)
Other versions
EP3150855A1 (de
EP3150855A4 (de
Inventor
Yoshiaki Miyamoto
Yoshiyuki Kimata
Toshiyuki Goto
Hajime Sato
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.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries 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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP3150855A1 publication Critical patent/EP3150855A1/de
Publication of EP3150855A4 publication Critical patent/EP3150855A4/de
Application granted granted Critical
Publication of EP3150855B1 publication Critical patent/EP3150855B1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/109—Lubrication
    • 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
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation

Definitions

  • the present invention relates to an open-type compressor which is provided on an outer circumference of a drive shaft and can supply oil which is pumped up by an oil supply pump driven by the drive shaft to a sliding part through an oil supply passage which is pierced inside the drive shaft along an axial direction.
  • a centrifugal-type oil supply pump, a displacement-type oil supply pump, or the like is provided on the end of a drive shaft, a lubricant which fills a sealed vessel is pumped up by the oil supply pump, and the oil is supplied to a sliding part through an oil supply passage which is pierced inside the drive shaft along the axial direction.
  • Patent Document 2 discloses a forcible oil-supply type compressor in which the oil supply passage pierced inside the drive shaft along the axial direction is provided so as to be offset with respect to the axis by a predetermined dimension and oil supply performance is improved using a centrifugal force.
  • the present invention is made in consideration of the above-described circumstances, and an object thereof is to provide an open-type compressor in which a decrease in the oil supply amount due to an increase of the flow-path pressure loss can be prevented particularly in the high rotational speed range, and reliability with respect to lubrication performance can be improved.
  • an open-type compressor including: a drive shaft which is rotatably supported inside a housing and includes one end which protrudes outside the housing; an oil supply pump which is provided on an outer circumferential section of the drive shaft and is driven by rotation of the drive shaft; a pump chamber which is formed around the drive shaft and into which oil pumped up by the oil supply pump is discharged; an axial-direction oil supply passage which is pierced inside the drive shaft along the direction of an axis of the axial-direction oil supply passage, and through which oil from the pump chamber is supplied to a sliding part; and a radial-direction oil supply passage which is provided in the drive shaft and through which oil in the pump chamber is introduced to the axial-direction oil supply passage, in which the axial-direction oil supply passage is provided at a position which is decentered by a predetermined dimension with respect to the axis of the drive shaft, and the radial-direction oil supply passage is provided on a side toward
  • the axial-direction oil supply passage which is pierced inside the drive shaft is provided at the position decentered by a predetermined dimension with respect to the axis of the drive shaft, and the radial-direction oil supply passage through which oil in the pump chamber pumped up by the oil supply pump is introduced to the axial-direction oil supply passage is provided in the direction in which the axial-direction oil supply passage is decentered.
  • the passage length of the radial-direction oil supply passage decreases as the axial-direction oil supply passage is decentered and the radial-direction oil supply passage is provided on the decentered side, and it is possible to decrease flow-path pressure loss due to a centrifugal force generated in an inlet portion of the radial-direction oil supply passage. That is, the passage length of the radial-direction oil supply passage becomes the radius of the drive shaft if the axial-direction oil supply passage is not decentered.
  • the passage length can be shorter than the radius of the drive shaft, and it is possible to decrease the flow-path pressure loss according to the decrease in the passage length.
  • the axial-direction oil supply passage is decentered by the predetermined dimension, and it is possible to increase oil supply performance with respect to the sliding part using centrifugal pump effects acting on the oil in the axial-direction oil supply passage.
  • the radial-direction oil supply passage may be provided at a position at which a passage length is shortest on the axis in the decentered direction.
  • the passage length of the radial-direction oil supply passage can be decreased by the degree corresponding to the decentered dimension of the axial-direction oil supply passage, and the passage length becomes the shortest length. Therefore, it is possible to minimize the flow-path pressure loss due to the centrifugal force generated in the inlet portion of the radial-direction oil supply passage. Accordingly, it is possible to improve the oil supply amount in the high rotational speed range and to further improve the oil supply performance.
  • a passage diameter of the axial-direction oil supply passage may be greater than a passage diameter of the radial-direction oil supply passage.
  • the passage diameter of the axial-direction oil supply passage is greater than the passage diameter of the radial-direction oil supply passage, it is possible to easily obtain centrifugal pump effects due to decentering and to decrease the flow-path pressure loss in the passage.
  • the radial-direction oil supply passage and the axial-direction oil supply passage such that these communicate with each other such that steps, burrs, and the like do not occur, it is possible to prevent flow-path pressure loss from occurring in the connection portion between the radial-direction oil supply passage and the axial-direction oil supply passage, and it is possible to prevent the oil supply amount from decreasing in the high rotational speed range and to improve the oil supply performance.
  • the passage length of the radial-direction oil supply passage decreases as the axial-direction oil supply passage is decentered and the radial-direction oil supply passage is provided on the decentered side, and it is possible to decrease flow-path pressure loss due to a centrifugal force generated in the inlet portion of the radial-direction oil supply passage.
  • the axial-direction oil supply passage is decentered by the predetermined dimension, and it is possible to increase oil supply performance with respect to the sliding part using centrifugal pump effects acting on the oil in the axial-direction oil supply passage, according to synergistic effects between the decreasement in the flow-path pressure loss in the radial-direction oil supply passage and the improvement of oil supply performance in the axial-direction oil supply passage, it is possible to prevent the oil supply amount from decreasing particularly in a high rotational speed range, and it is possible to increase reliability with respect to lubrication performance.
  • Fig. 1 is a longitudinal sectional view of an open-type compressor according to the embodiment of the present invention
  • Fig. 2A is a sectional view of a drive shaft
  • Fig. 2B is a right-side view of the drive shaft
  • Figs. 3 and 4 are sectional views taken along line a-a of Fig. 2A .
  • the open-type compressor 1 includes a tubular housing 2 in which a bottomed front housing 3 and a bottomed rear housing 4 are integrally connected to each other by a bolt 5.
  • a bearing member 6 is fixed and installed to the opening end side in the housing 2 on the front housing 3 side by a bolt 7, and a drive shaft 9 is rotatably supported by a radial bearing portion 6A of the bearing member 6 and a rolling bearing 8 which is installed in the front housing 3.
  • One end of the drive shaft 9 penetrates the front housing 3 and protrudes outside the front housing 3, and driving power from an external drive source such as an engine is input to the protrusion portion of the drive shaft 9 via a pulley 10 and an electromagnetic clutch 11.
  • the pulley 10 is rotatably supported to an outer circumference of a flange member 13, which is fixed and installed to the front end surface of the front housing 3 by a bolt 12, via a rolling bearing 14, and a coil assembly 15 of the electromagnetic clutch 11 is incorporated into the pulley 10.
  • an armature assembly 16 of the electromagnetic clutch 11 is assembled to the external protrusion end of the drive shaft 9 by a bolt 17 via a boss portion so as to face the pulley 10.
  • a mechanical seal 18 for hermetically sealing the penetration portion of the drive shaft 9 is installed on the inner circumference of the flange member 13.
  • a compression mechanism 19 is incorporated into the rear housing 4 side of the housing 2.
  • the compression mechanism 19 is a scroll compression mechanism 19 which includes a pair of fixed scroll 20 and orbiting scroll 21.
  • the pair of fixed scroll 20 and orbiting scroll 21 engage with each other so as to be deviated by a phase of 180°, multiple compression chambers 22 are formed between both scrolls 20 and 21, and the scroll compression mechanism 19 is known.
  • the fixed scroll 20 is fastened and fixed to the bearing member 6 by a bolt 23, and a discharge cavity 26 is formed between the back face of the end plate of the fixed scroll and the inner surface of the rear housing 4.
  • a discharge port 24 which discharges compressed gas into the discharge cavity 26 and a discharge valve 25 which opens and closes the discharge port 24 are provided on the end plate of the fixed scroll 20.
  • a discharge port 27 through which compressed gas which has been discharged into the discharge cavity 26 is discharged to the outside is open to the rear housing 4, and a discharge pipe configuring a refrigerating cycle can be connected to the rear housing 4.
  • the orbiting scroll 21 has a boss portion 28 on the back face of the end plate of the orbiting scroll 21, a crank pin 9A provided on the inner end side of the drive shaft 9 is connected to the boss portion 28 via a drive bush 29 and a turning bearing 30, and the orbiting scroll 21 is pivotally driven via the crank pin 9A by the rotation of the drive shaft 9.
  • the back face of the end plate of the orbiting scroll 21 is supported by a thrust bearing 31 provided in the bearing member 6, the rotation of the orbiting scroll 21 is prevented by a known rotation prevention mechanism 32 including an oldham link, a pin ring, or the like which is interposed between the back plate of the end plate and the bearing member 6, and the orbiting scroll 21 is driven so as to be pivotally revolved with respect to the fixed scroll 20.
  • the compression mechanism 19 is a so-called stepped scroll compression mechanism 19 in which a step portion which changes a lap height is provided in spiral directions of the fixed scroll 20 and the orbiting scroll 21, the outer circumferential side lap height is higher than the inner circumferential side lap height, gas can be compressed not only in the circumferential direction but also in the axial direction, and a three-dimensional compression can be realized.
  • the present invention is not limited to this.
  • the inside of the front housing 3 is filled with a lubricant having a required amount, the lower space inside the front housing 3 becomes an oil sump 35, and oil is collected in the oil sump 35.
  • the oil in the oil sump 35 is suctioned to an oil supply pump 37 via an intake passage 36.
  • the oil supply pump 37 is a known a rotary-type displacement pump in which a decentered portion 9B ( Fig. 2 ) is formed on the outer circumferential section of the drive shaft 9 penetrating the front end surface of the front housing 3, and a rotor 38 which is rotated so as to be decentered in the cylinder formed between the front end surface of the front housing 3 and the end surface of the flange member 13 is fitted to the decentered portion 9B.
  • the oil which is pumped up from the oil sump 35 by the oil supply pump 37 is discharged into a pump chamber 39 which is formed between the decentered portion 9B around the drive shaft 9 and the mechanical seal 18.
  • the oil pumped to the pump chamber 39 is supplied to a sliding part such as the radial bearing portion 6A, the drive bush 29, the turning bearing 30, or the thrust bearing 31, a sliding part such as the mechanical seal 18, or the like through a radial-direction oil supply passage 40 and an axial-direction oil supply passage 41 which are provided inside the drive shaft 9.
  • the axial-direction oil supply passage 41 which is provided along the axis L of the drive shaft 9 is inside the drive shaft 9 at a position decentered to an axis L of the drive shaft 9 by a predetermined dimension (decentered dimension) ⁇ h.
  • the radial-direction oil supply passage 40 through which the oil inside the pump chamber 39 is introduced to the axial-direction oil supply passage 41 is provided in the decentered direction of the axial-direction oil supply passage 41.
  • the radial-direction oil supply passage 40 is provided at the position at which a passage length h1 thereof is shortest on the axis in the decentered direction.
  • a radial-direction oil supply passage 40A may be provided in a direction which has a predetermined angle with respect to the axis in the decentered direction.
  • a passage length h2 of the radial-direction oil supply passage 40A can be shorter than the passage length h with which the axial-direction oil supply passage 41 is provided on the axis L of the drive shaft 9, and in this case, the passage h2 satisfies that h1 ⁇ h2 ⁇ h.
  • the radial-direction oil supply passage through which the oil in the pump chamber 39 is introduced to the axial-direction oil supply passage 41 is not limited to be positioned on the axis in the decentered direction, the radial-direction oil supply passage is provided on the decentered side of the axial-direction oil supply passage 41, and the passage length of the radial-direction oil supply passage can be shorter than that when the axial-direction oil supply passage 41 is provided on the axis L of the drive shaft 9.
  • the axial-direction oil supply passage 41 is a blind hole which is pierced along the axis L from one end of the crank pin 9A.
  • the radial-direction oil supply passages 40 and 40A are hole which are provided to be radially perpendicular in the vicinity of the tip portion of the blind hole, and it is necessary to prevent steps, burrs, or the like generating flow-path pressure loss from occurring in the intersection portion (connection portion) between the axial-direction oil supply passage 41 and the radial-direction oil supply passages 40 and 40A.
  • a passage diameter d1 of the axial-direction oil supply passage 41 to be greater than a passage diameter d2 of each of the radial-direction oil supply passages 40 and 40A (d1 > d2), it is possible to easily obtain centrifugal pump effect due to decentering in the axial-direction oil supply passage 41 and to decrease the flow-path pressure loss in the passage, and both passages 40 and 40A, and 41 can be processed to communicate with each other such that steps, burrs, and the like do not occur in the connection portion between both passages 40 an 40A, and 41.
  • the orbiting scroll 21 of the scroll compression mechanism 19 is driven so as to be pivotally revolved around the fixed scroll 20
  • low-pressure gas suctioned from the intake port 33 into the intake cavity 34 is suctioned into the compression chamber 22 and is compressed so as to be high-pressure gas
  • the high-pressure gas is discharged from the discharge port 24 into the discharge cavity 26 and discharged from the discharge port 27 to the refrigerating cycle.
  • a lubricant in the oil sump 35 is suctioned via the intake passage 36 by the oil supply pump 37 driven by the rotation of the drive shaft 9, and is pumped to the pump chamber 39.
  • the oil pumped into the pump chamber 39 lubricates the sliding part of the mechanical seal 18, is introduced into the axial-direction oil supply passage 41 via the radial-direction oil supply passages 40 and 40A, and is supplied to the sliding part such as the radial bearing portion 6A, the drive bush 29, the turning bearing 30, or the thrust bearing 31 through the axial-direction oil supply passage 41 so as to lubricate the sliding part.
  • the oil which has lubricated the sliding part is collected in the oil sump 35 which is the bottom portion of the housing 2 and is recirculated.
  • the axial-direction oil supply passage 41 is provided at the position which is decentered to the axis L of the drive shaft 9 by the predetermined dimension ⁇ h, and the radial-direction oil supply passages 40 and 40A through which the oil in the pump chamber 39 is introduced to the axial-direction oil supply passage 41 is introduced are provided on the decentered side of the axial-direction oil supply passage 41. Accordingly, the passage lengths h1 and h2 can be shorter than those in the case where the axial-direction oil supply passage 41 is provided on the axis L of the drive shaft 9 (h1 ⁇ h2 ⁇ h).
  • the passage lengths h1 and h2 of the radial-direction oil supply passages 40 and 40A can be shortened by the dimension ⁇ h by which the axial-direction oil supply passage 41 is decentered, and it is possible to decrease the flow-path pressure loss due to the centrifugal force generated in the inlet portions of the radial-direction oil supply passages 40 and 40A.
  • the axial-direction oil supply passage 41 is decentered by the predetermined dimension ⁇ h, it is possible to increase oil supply performance with respect to the sliding part using centrifugal pump effects acting on the oil in the axial-direction oil supply passage 41.
  • Fig. 5 is a graph showing oil supply characteristics in the case where the forcible oil-supply type compressor is adopted, in which a horizontal axis indicates a rotating speed (rpm) of the drive shaft 9 and a vertical axis indicates an oil supply amount (cm 3 /min).
  • a horizontal axis indicates a rotating speed (rpm) of the drive shaft 9
  • a vertical axis indicates an oil supply amount (cm 3 /min).
  • the axial-direction oil supply passage 41 is provided so as to be decentered to the axis L
  • the radial-direction oil supply passages 40 and 40A are provided on the decentered side, and the passage lengths h1 and h2 are shortened, the oil supply amount is improved in the high rotational speed range as shown by plots ⁇ and can approach the theoretical value.
  • the radial-direction oil supply passage 40 is provided at the position at which the passage length h1 is shortest on the axis in the decentered direction. Accordingly, the passage length h1 of the radial-direction oil supply passage 40 can be decreased by the degree corresponding to the decentered dimension ⁇ h of the axial-direction oil supply passage 41, and the passage length h1 becomes the shortest length. Therefore, it is possible to minimize the flow-path pressure loss due to the centrifugal force generated in the inlet portion of the radial-direction oil supply passage 40. Accordingly, it is possible to improve the oil supply amount in the high rotational speed range and to further improve the oil supply performance.
  • the open-type compressor 1 according to the present embodiment is applied to an open-type scroll compressor 1 which adopts the forcible oil-supply type compressor which is operated at a high speed of 3600 rpm or more, it is possible to improve lubrication performance.
  • the present invention is not limited to the invention according to the present embodiment, and may be appropriately modified within the scope of the claims.
  • the open-type compressor 1 the example in which the scroll type compressor is applied is described.
  • other-type compressors for example, a rotary open-type compressor, a swash plate open-type compressor, a reciprocating open-type compressor, or the like may be similarly applied.
  • the present invention is not limited to this, and other type oil supply pumps such as a screw type pump may be applied.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Rotary Pumps (AREA)

Claims (3)

  1. Offener Verdichter (1), der Folgendes umfasst:
    eine Antriebswelle (9), die drehbar in einem Gehäuse (2) gestützt wird und ein Ende beinhaltet, das aus dem Gehäuse (2) ragt;
    eine Ölzufuhrpumpe (37), die auf einem Außenumfangsbereich der Antriebswelle (9) bereitgestellt ist und durch Drehung der Antriebswelle (9) angetrieben wird;
    eine Pumpenkammer (39), die um die Antriebswelle (9) gebildet ist und aus der Öl, das von der Ölzufuhrpumpe (37) hinaufgepumpt wird, ausgegeben wird;
    einen Axialrichtungsölzufuhrkanal (41), der die Antriebswelle (9) entlang der Richtung einer Achse des Axialrichtungsölzufuhrkanals durchdringt und durch den Öl von der Pumpenkammer (39) einem Gleitteil zugeführt wird; und
    einen Radialrichtungsölzufuhrkanal (40, 40A), der in der Antriebswelle (9) bereitgestellt ist,
    dadurch gekennzeichnet, dass das Öl in der Pumpenkammer (39) durch den Radialrichtungsölzufuhrkanal (40, 40A) in den Axialrichtungsölzufuhrkanal (41) eingeleitet wird,
    wobei der Axialrichtungsölzufuhrkanal (41) an einer Position bereitgestellt ist, die mit Bezug auf die Achse der Antriebswelle (9) um ein vorbestimmtes Maß von der Mitte abweicht, und
    wobei der Radialrichtungsölzufuhrkanal (40, 40A) auf einer Seite bereitgestellt ist, zu der der Axialrichtungsölzufuhrkanal (41) von der Mitte abweicht.
  2. Offener Verdichter nach Anspruch 1,
    wobei der Radialrichtungsölzufuhrkanal (41) an einer Position bereitgestellt ist, an der eine Kanallänge (h1) auf der Achse in der Mittenabweichungsrichtung am kürzesten ist.
  3. Offener Verdichter nach Anspruch 1 oder 2,
    wobei ein Kanaldurchmesser (d1) des Axialrichtungsölzufuhrkanals (41) größer ist als ein Kanaldurchmesser (d2) des Radialrichtungsölzufuhrkanals (40, 40A).
EP15829255.7A 2014-08-08 2015-08-04 Offener verdichter Active EP3150855B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014162441A JP6462265B2 (ja) 2014-08-08 2014-08-08 開放型圧縮機
PCT/JP2015/072069 WO2016021590A1 (ja) 2014-08-08 2015-08-04 開放型圧縮機

Publications (3)

Publication Number Publication Date
EP3150855A1 EP3150855A1 (de) 2017-04-05
EP3150855A4 EP3150855A4 (de) 2017-06-28
EP3150855B1 true EP3150855B1 (de) 2020-04-22

Family

ID=55263852

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15829255.7A Active EP3150855B1 (de) 2014-08-08 2015-08-04 Offener verdichter

Country Status (6)

Country Link
EP (1) EP3150855B1 (de)
JP (1) JP6462265B2 (de)
KR (2) KR102096139B1 (de)
CN (1) CN106662093A (de)
AU (1) AU2015300143B2 (de)
WO (1) WO2016021590A1 (de)

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04279792A (ja) * 1991-03-08 1992-10-05 Toshiba Corp 流体圧縮機
JPH05149277A (ja) * 1991-11-26 1993-06-15 Mitsubishi Heavy Ind Ltd 横置型密閉スクロール圧縮機
JPH08219063A (ja) 1995-02-13 1996-08-27 Daikin Ind Ltd 回転軸の潤滑油供給構造
CN2688935Y (zh) * 2004-01-21 2005-03-30 柳州高新区浦发汽车空调有限公司 容积式涡旋流体压缩装置
JP4301985B2 (ja) * 2004-03-29 2009-07-22 三菱重工業株式会社 スクロール圧縮機
JP2012097577A (ja) * 2010-10-29 2012-05-24 Daikin Industries Ltd 圧縮機
CN202520559U (zh) * 2012-03-14 2012-11-07 广东美芝精密制造有限公司 滚动转子式压缩机的曲轴结构

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
AU2015300143B2 (en) 2018-05-10
JP2016037922A (ja) 2016-03-22
EP3150855A1 (de) 2017-04-05
WO2016021590A1 (ja) 2016-02-11
KR20170010406A (ko) 2017-01-31
EP3150855A4 (de) 2017-06-28
CN106662093A (zh) 2017-05-10
JP6462265B2 (ja) 2019-01-30
KR20180112091A (ko) 2018-10-11
KR102096139B1 (ko) 2020-04-01
AU2015300143A1 (en) 2017-01-19

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