EP3409948A1 - Hermetic two-stage compressor - Google Patents
Hermetic two-stage compressor Download PDFInfo
- Publication number
- EP3409948A1 EP3409948A1 EP17782527.0A EP17782527A EP3409948A1 EP 3409948 A1 EP3409948 A1 EP 3409948A1 EP 17782527 A EP17782527 A EP 17782527A EP 3409948 A1 EP3409948 A1 EP 3409948A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- housing
- oil
- stage
- bearing
- hermetic
- 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.)
- Granted
Links
- 238000003860 storage Methods 0.000 claims abstract description 9
- 230000006835 compression Effects 0.000 claims description 54
- 238000007906 compression Methods 0.000 claims description 54
- 239000003507 refrigerant Substances 0.000 abstract description 52
- 239000003921 oil Substances 0.000 description 111
- 230000007423 decrease Effects 0.000 description 32
- 230000003247 decreasing effect Effects 0.000 description 8
- 230000002093 peripheral effect Effects 0.000 description 6
- 230000004308 accommodation Effects 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 238000000926 separation method Methods 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 239000011347 resin Substances 0.000 description 2
- 229920005989 resin Polymers 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 238000007792 addition Methods 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
Images
Classifications
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- 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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
-
- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/005—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of dissimilar working principle
-
- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- 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
-
- 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
- F04C29/026—Lubricant separation
-
- 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
-
- 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
-
- 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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/20—Flow
Abstract
Description
- The present invention relates to a hermetic two-stage compressor.
- Priority is claimed on Japanese Patent Application No.
2016-081000, filed April 14, 2016 - In the related art, for example, a hermetic two-stage compressor is known, which is used for refrigeration air conditioning and includes a low stage-side compression section and a high stage-side compression section which are sealed in a housing. In addition, an example of the hermetic two-stage compressor is disclosed in PTL 1.
- In the hermetic two-stage compressor of PTL 1, a rotary compressor is disposed as a low stage-side compression section, a scroll compressor is disposed as a high stage-side compression section, a gas supplied into a housing is compressed by the rotary compressor, and thereafter, the gas is further compressed by the scroll compressor to be discharged from the housing. The hermetic two-stage compressor is operated in a state where a lubricating oil of the low stage-side compression section and the high stage-side compression section is held in the housing.
- Here, in the hermetic two-stage compressor disclosed in PTL 1, a bearing bracket is provided in a divided portion of an upper and lower split type housing, and an oil circulation amount (OC%) in a refrigerating cycle is reduced by allowing the gas in a central region where an oil content is small to flow into the scroll compressor while preventing the gas in an outer peripheral region inside the housing containing a lot of oil from flowing into the scroll compressor.
- [PTL 1] Japanese Unexamined Patent Application Publication No.
2009-180107 - However, in the bearing bracket of PTL 1, in a case where a member for decreasing the oil circulation amount (OC%) in the refrigerating cycle is provided in the housing by welding, there is a possibility that strain occurs in the housing. Accordingly, it is difficult to accurately manufacture the hermetic two-stage compressor, and it takes time and labor to manufacture. In addition, the bearing bracket of the hermetic two-stage compressor of PTL 1 receives a load from a bearing case, and thus, it is necessary to increase a thickness so as to secure strength. As a result, an internal volume of the housing decreases, which is disadvantageous when oil is separated from the gas.
- Accordingly, the present invention is to provide a hermetic two-stage compressor capable of being easily manufactured and effectively separating oil from a gas. Solution to Problem
- According to a first aspect of the present invention, there is provided a hermetic two-stage compressor including: a housing which includes an oil storage inside the housing; a rotary shaft which is disposed in the housing; a motor which is disposed in the housing so as to rotate the rotary shaft and includes a stator which is provided on a radially outer side and a rotor which is provided on a radially inner side; a low stage-side compression section which is disposed on one side (a first end side) in an axial direction of the rotary shaft with respect to the motor in the housing and is connected to the rotary shaft so as to compress a gas; a bearing device which is disposed on the other side (a second end side) in the axial direction with respect to the motor in the housing and includes a bearing which supports the rotary shaft and a bearing casing which supports the bearing to the housing; and a high stage-side compression section which is disposed on the other side (the second end side) in the axial direction with respect to the bearing device and further compresses the gas discharged from the low stage-side compression section, in which the bearing casing includes a suction channel which is provided to suck the gas into the high stage-side compression section and includes a suction opening which is open to the one side (first end side) in the axial direction, and a restricting surface which is disposed between the suction opening and the motor and is provided toward the radially inner side from an inner surface of the housing so as to restrict a flow of the gas to the suction opening on the radially outer side.
- In the hermetic two-stage compressor, the oil of the oil storage and the gas are compressed in the low stage-side compression section. Accordingly, the oil is contained in the gas which is discharged from the low stage-side compression section. A portion of the gas containing the oil flows out toward the motor, and thereafter, flows to the high stage-side compression section through the gap between the stator and the rotor or a through-hole provided in the rotor. In addition, when the gas passes through the motor, the oil in the gas comes into contact with the rotor or an oil separation plate provided above the rotor, and thus, a content of the oil in the gas decreases. Meanwhile, the gas which has passed through a portion between the stator and the housing does not come into contact with the rotor and flows toward the high stage-side compression section as it is. Accordingly, the gas flows toward the high stage-side compression section in a state where the content of the oil in the gas is high. That is, the amount of the oil in the gas discharged from the low stage-side compression section decreases on the radially inner side of the housing and increases on the radially outer side thereof.
- Here, in the present aspect, according to a simple method in which the restricting surface is provided in the bearing casing, the flow of the gas to the suction opening on the radially outer side can be restricted. Therefore, it is possible to prevent the gas having a high content of oil on the radially outer side flows into the suction channel through suction opening as it is, and the gas on the radially inner side having a low content of oil can flow into the suction channel through the suction opening. As a result, it is possible to supply the gas having a low content of oil to the high stage-side compression section, and it is possible to decrease the amount of the oil in the gas which is compressed by the high stage-side compression section and is discharged therefrom. Therefore, it is possible to decrease an oil circulation amount (OC%) in a system including the hermetic two-stage compressor.
- In addition, if the gas on the radially outer side comes into contact with the restricting surface, the oil in the gas is attached to the restricting surface, and the gas in which the content of the oil has decreased is guided to the radially inner side by the restricting surface and flows from the suction opening into the suction channel. Accordingly, in a state where the amount of the oil in the gas is decreased by the restricting surface, the gas is supplied from the suction channel to the high stage-side compression section, and thus, it is possible to decrease the amount of the oil in the gas which is compressed by the high stage-side compression section and is discharged therefrom, and it is possible to decrease the oil circulation amount (OC%) in the system.
- Moreover, in the first aspect, the hermetic two-stage compressor according to a second aspect of the present invention may further include an inflow restricting plate which is fixed to the bearing casing, is formed in a plate shape, and includes the restricting surface on the one side (first end side) of the axial direction.
- In this way, the inflow restricting plate is provided in the bearing casing, and thus, it is possible to provide the restricting surface in the bearing casing. Therefore, compared to a case where a member corresponding to the inflow restricting plate is attached to the housing so as to provide the restricting surface, it is possible to very easily provide the restricting surface in the bearing casing. In addition, it is possible to easily provide the restricting surface in the existing bearing casing.
- Moreover, in the hermetic two-stage compressor according to a third aspect of the present invention, in the first or second aspect, the restricting surface may include a flat surface which is provided on an end portion on the radially outer side which is an inner surface side of the housing and is perpendicular to the axis to be formed in an annular shape about the axis and an inclined surface which is inclined toward the one side (first end side) in the axial direction from the flat surface toward the radially inner side so as to be formed in a truncated conical shape about the axis.
- In this way, the inclined surface which is formed in a truncated conical shape is provided as the restricting surface, and thus, it is possible to form the opening portion which is formed in an annular shape about the axis so as to extend from the suction opening to the one side (first end side) in the axial direction. Accordingly, the opening portion extending from the suction opening can be formed in an annular shape, and thus, an opening area can be secured, and it is possible to secure a flow rate of the gas flowing from the inside of the housing into the suction channel. In addition, the gas having a high content of oil in the radially outer side region flows to the radially inner side along the flat surface of the restricting surface, and thereafter, collides with the inclined surface, and thus, the oil can be attached to the inclined surface. Accordingly, the gas flows into the suction channel in a state where the content of the oil in the gas further decreases, and thus, it is possible to decrease the amount of the oil in the gas supplied to the high stage-side compression section, and it is possible to decrease the amount of the oil in the gas which is compressed by the high stage-side compression section and is discharged therefrom. Accordingly, it is possible to further decrease the oil circulation amount (OC%) in the system.
- Moreover, in the hermetic two-stage compressor according to a fourth aspect of the present invention, in any one of the first to third aspects, an inner edge portion on the radially inner side of the restricting surface may be disposed at a position on the radially inner side of the stator, and the restricting surface may close a portion of the suction opening so as to secure an intake amount of the gas required in the high stage-side compression section.
- In this way, the inner edge portion of the restricting surface is positioned on the radially inner side from the stator, and thus, the restricting surface extends to the position of the rotor. Accordingly, the gas which comes into contact with the rotor so as to sufficiently decrease the amount of the oil can flow from the suction opening into the suction channel. Therefore, it is possible to further decrease the amount of the oil in the gas which is compressed by the high stage-side compression section and is discharged therefrom, and it is possible to further decrease the oil circulation amount (OC%) in the system. Moreover, at this case, it is possible to secure an intake amount of the gas required in the high stage-side compression section, and it is possible to prevent compression efficiency in the high stage-side compression section from decreasing.
- In addition, in any one of the first to fourth aspects, the hermetic two-stage compressor according to a fifth aspect of the present invention may further include a seal member which is provided in a gap between an outer edge portion on the radially outer side of the restricting surface and the inner surface of the housing.
- The gas having a high content of oil which has passed through a portion between the housing and the stator in the radially outer side region in the housing can be prevented from flowing from the portion between the restricting surface and the housing into the high stage-side compression section as it is, by the seal member. Accordingly, it is possible to further decrease the amount of the oil in the gas which is compressed by the high stage-side compression section and is discharged therefrom, and it is possible to further decrease the oil circulation amount (OC%) in the system.
- In addition, in any one of the first to fifth aspects, the hermetic two-stage compressor according to a sixth aspect of the present invention may further include an oil return section which is provided at a position of an end portion on the radially outer side in the bearing casing and causes the high stage-side compression section and the one side (first end side) in the axial direction from the bearing casing in the housing to communicate with each other such that oil from the high stage-side compression section can flow through the oil return section.
- The oil return section is provided, and thus, the oil used for lubricating in the high stage-side compression section is returned into the housing through the oil return section. Accordingly, it is possible to further decrease the amount of the oil in the gas which is compressed by the high stage-side compression section and is discharged therefrom, and it is possible to further decrease the oil circulation amount (OC%) in the system.
- In addition, the oil return section is provided on the end portion on the radially outer side of the bearing casing, and thus, the oil return section is provided at a position separated from the suction opening which is open to the radially inner side. Therefore, the oil which is returned from the oil return section to the housing can be prevented from flowing from the suction opening into the suction channel as it is. Accordingly, it is possible to further decrease the amount of the oil in the gas which is compressed by the high stage-side compression section and is discharged therefrom, and it is possible to further decrease the oil circulation amount (OC%) in the system.
- Moreover, in the hermetic two-stage compressor according to a seventh aspect of the present invention, in any one of the first to sixth aspects, an accommodation portion which extends in the axial direction and through which a wire of the motor can be inserted may be provided in the bearing casing, and the hermetic two-stage compressor may further include a seal member which is provided in a gap between the restricting surface and the wire of the motor.
- Even when the accommodation portion into which the wire of the motor is inserted is formed in the bearing casing, the gap between the restricting surface and the wire of the motor can be sealed by the seal member. Accordingly, it is possible to prevent the gas containing the oil from being supplied to the high stage-side compression section through the gap as it is.
- According to the hermetic two-stage compressor, the method of providing the restricting surface in the bearing casing is used, and thus, it is possible to easily manufacture the hermetic two-stage compressor, and it is possible to effectively separate the oil in the gas by the restricting surface.
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Fig. 1 is a longitudinal sectional view showing a hermetic two-stage compressor according to a first embodiment of the present invention. -
Fig. 2 shows the hermetic two-stage compressor according to the first embodiment of the present invention and is a longitudinal sectional view at a sectional position from the sectional position ofFig. 1 in a circumferential direction. -
Fig. 3 is a view showing a bearing casing and an inflow restricting plate of the hermetic two-stage compressor according to the first embodiment of the present invention and shows a cross section taken along line I-I ofFig. 1 . -
Fig. 4 is a longitudinal sectional view showing a hermetic two-stage compressor according to a second embodiment of the present invention. -
Fig. 5 is a view showing a bearing casing and an inflow restricting plate of the hermetic two-stage compressor according to the second embodiment of the present invention and shows a cross section taken along line IV-IV ofFig. 4 . -
Fig. 6 is a view showing a bearing casing and an inflow restricting plate of a hermetic two-stage compressor according to a modification example of the embodiment of the present invention. - Hereinafter, a hermetic two-stage compressor 1 (hereinafter, referred to as a two-stage compressor 1) according to a first embodiment of the present invention will be described.
- As shown in
Figs. 1 and2 , for example, the two-stage compressor 1 compresses a refrigerant R which is a gas such as carbon dioxide. The two-stage compressor 1 includes ahousing 11, a rotary compressor (low stage-side compression section) 12, a scroll compressor (high stage-side compression section) 13, anelectric motor 14, arotary shaft 15, and abearing device 30 which are provided inside thehousing 11, and aninflow restricting plate 61 which is fixed to thebearing device 30. - The
housing 11 includes amain body portion 21 which is formed in a cylindrical shape, and anupper cover portion 22 and alower cover portion 23 which close an upper opening and a lower opening of themain body portion 21. In addition, a space inside thehousing 11 is sealed. - The
rotary shaft 15 is disposed to extend vertically inside thehousing 11. - The
electric motor 14 is disposed on an outer peripheral side of therotary shaft 15 and rotates therotary shaft 15 around an axis X. That is, theelectric motor 14 includes arotor 38 which is fixed to an outer peripheral surface of therotary shaft 15, and astator 39 which radially faces therotor 38 with a gap between thestator 39 and the outer peripheral surface of therotor 38 and is fixed to an inner surface of themain body portion 21 of thehousing 11. - The
electric motor 14 is connected to a power source (not shown) via awire 14a and rotates therotary shaft 15 by power from the power source. A portion of thestator 39 in a circumferential direction is fixed to the inner surface of thehousing 11, and in portions other than the portion fixed to the inner surface of thehousing 11, the inner surface of thehousing 11 and thestator 39 are disposed with a gap S in a radial direction. - The
rotary compressor 12 is disposed at a position adjacent to thelower cover portion 23 at a lower portion which is one in a direction of the axis X of theelectric motor 14 inside thehousing 11. Therotary compressor 12 includes aneccentric shaft portion 41 which is provided on therotary shaft 15, apiston rotor 42 which is fixed to theeccentric shaft portion 41 and is eccentrically rotated about the axis X according to a rotation of therotary shaft 15, and acylinder 44 which includes a compression chamber C1 accommodating thepiston rotor 42 is formed inside thecylinder 44. - A
suction hole 44a through which the refrigerant R can flow into thecylinder 44 is formed in thecylinder 44. Asuction pipe 33 which is provided to penetrate themain body portion 21 of thehousing 11 is connected to thesuction hole 44a and the refrigerant R is supplied through thesuction pipe 33 from the outside of thehousing 11. In addition, a discharge hole (not shown) is formed in thecylinder 44, and the refrigerant R compressed by therotary compressor 12 is discharged from the discharge hole to a region in thehousing 11 in which theelectric motor 14 is provided. - In addition, oil A is stored in the bottom portion of the
housing 11 and anoil storage 01 is provided in the bottom portion. When the oil A is initially sealed, a liquid surface of theoil storage 01 is positioned above therotary compressor 12. Accordingly, therotary compressor 12 is driven in theoil storage 01. - The
scroll compressor 13 is disposed above theelectric motor 14 inside thehousing 11. Thescroll compressor 13 includes a fixedscroll 51 which is fixed to anupper bearing 31 and anorbiting scroll 57 which is disposed to face the fixedscroll 51 below the fixedscroll 51. - The fixed
scroll 51 includes anend plate 52 which is fixed to an upper surface of theupper bearing 31 and afixed lap 53 which protrudes downward from theend plate 52. Adischarge hole 52a which vertically penetrates theend plate 52 is formed at a center portion (in the vicinity of the axis X) of theend plate 52. - The orbiting
scroll 57 includes anend plate 58 which is disposed to be interposed between the bearing device 30 (upper bearing 31 described below) and theend plate 52 of the fixedscroll 51 in the direction of the axis X and is fixed to therotary shaft 15, and anorbiting lap 59 which protrudes upward from theend plate 58. - The
end plate 58 is fixed to aneccentric shaft portion 56 provided on an upper end of therotary shaft 15 and is eccentrically rotated about the axis X according to the rotation of therotary shaft 15. - The orbiting
lap 59 meshes with the fixedlap 53, and thus, a compression chamber C2 in which the refrigerant R is compressed is formed between the orbitinglap 59 and the fixedlap 53. - Here, a suction hole (not shown) is formed in the fixed
scroll 51, and the refrigerant R which is compressed by therotary compressor 12 and is discharged into thehousing 11 can be sucked into the compression chamber C2 via thebearing device 30 through the suction hole. The refrigerant R compressed in the compression chamber C2 is discharged to the outside of thehousing 11 from adischarge pipe 34 through thedischarge hole 52a of the fixedscroll 51, and thedischarge pipe 34 is open to a space surrounded by the fixedscroll 51 fixed to the upper portion of the fixedscroll 51 in thehousing 11 and thedischarge cover 50 and is provided to penetrate thehousing 11 so as to extend the outside of thehousing 11. - The bearing
device 30 includes theupper bearing 31 which is provided on the upper portion of thehousing 11 inside thehousing 11, andlower bearings housing 11 inside thehousing 11. - The
lower bearings rotary shaft 15 with respect to thehousing 11 at the lower portion of thehousing 11. Specifically, therotary compressor 12 is vertically disposed in the direction of the axis X between thelower bearings lower bearings cylinder 44 by abolt 48. - The
upper bearing 31 includes abearing 31a which rotatably supports therotary shaft 15 around the axis X of therotary shaft 15 with respect to thehousing 11 and a bearingcasing 31b which supports thebearing 31a on thehousing 11 integrally with thebearing 31a. - As shown in
Figs. 1 to 3 , a plurality of suction channels FC are provided in the bearingcasing 31b, and the suction channels FC extend to be parallel to the axis X over the entire region of the bearingcasing 31b in the direction of the axis X with intervals to each other in the circumferential direction. In the present embodiment, each of the suction channels FC is a recessed groove having a rectangular cross section which is recessed from the outer peripheral surface of the bearingcasing 31b toward the radially inner side. - In addition, a suction opening FCa is provided in the bearing
casing 31b, and the suction opening FCa extends from a lower end of the suction channel FC toward the radially inner side so as to be continued to the lower side which is one side (first end side) of the axis X and is open in a fan shape downward when the bearingcasing 31b is viewed. - In addition, a recessed portion (accommodation portion) 31c is provided in the bearing
casing 31b, and the recessedportion 31c is recessed over the entire region in the direction of the axis X from the outer peripheral surface toward the radially inner side at a position at which the recessed portion does not interfere with the suction opening FCa. Thewire 14a of theelectric motor 14 is disposed inside the recessed portion. Aseal member 65 is provided in a gap among the recessedportion 31c, thewire 14a, and the inner surface of thehousing 11. For example, as theseal member 65, a seal material such as a resin can be used. - In addition, a bearing
channel 31d (refer toFig. 2 ) is formed in the bearingcasing 31b, and thebearing channel 31d radially penetrates the bearingcasing 31b and is open to the inside of thehousing 11 at a position in the direction of the axis X at which theorbiting scroll 57 is fixed to theeccentric shaft portion 56. - In addition, an oil return pipe (oil return section) 72 is provided in the bearing
casing 31b, and, at a position at which theoil return pipe 72 does not interfere with the suction opening FCa and the recessedportion 31c and a position of an end portion on the radially outer side, theoil return pipe 72 communicates with the bearingchannel 31d, penetrates the bearingcasing 31b toward theelectric motor 14 to extend along the inner surface of thehousing 11, and protrudes downward from the bearingcasing 31b. - As shown in
Fig. 3 , theinflow restricting plate 61 is fixed to the bearingcasing 31b bybolts 60 from below. Theinflow restricting plate 61 is formed in an annular shape about the axis X. Theinflow restricting plate 61 includes a plurality ofnotches 63, which are cut out from the end portion on the radially inner side toward the radially inner side, at positions corresponding to the suction openings FCa. A lower surface of theinflow restricting plate 61 becomes a restrictingsurface 62, and a bottom portion of eachnotch 63 forms aninner edge portion 62a of the restrictingsurface 62. Theinner edge portion 62a has a curved shape formed along the circumferential direction. Theinner edge portion 62a is positioned at a radially intermediate position of the suction opening FCa, and as a result, only the radially inner position of the suction opening FCa is open toward theelectric motor 14 by theinflow restricting plate 61. Accordingly, a flow of the refrigerant R to the suction opening FCa on the radially outer side is restricted by the restrictingsurface 62. - In addition, a
notch 61a is provided in theinflow restricting plate 61, and thenotch 61a is recessed from theouter edge portion 62b toward the radially inner side at a position corresponding to the position of thewire 14a so as not to interfere with thewire 14a. - As shown in
Fig. 1 , when viewed from a cross section including the axis X, the restrictingsurface 62 is provided to protrude from the inner surface of thehousing 11 toward the radially inner side. - In addition, in the present embodiment, a
seal member 66 is provided in a gap between the inner surface of thehousing 11 and anouter edge portion 62b (an end edge on the radially outer side along the inner surface of the housing 11) of the restrictingsurface 62. As theseal member 66, a seal member formed of a resin, an O ring, or the like can be used. - In the two-stage compressor 1 of the above-described present embodiment, the oil A of the
oil storage 01 and the refrigerant R are compressed by therotary compressor 12. Accordingly, the oil A is included in the refrigerant R discharged from therotary compressor 12. A portion of the refrigerant R including the oil A flows out toward theelectric motor 14, and thereafter, flows toward thescroll compressor 13 through the gap between thestator 39 and therotor 38 or the through-hole 37 provided in therotor 38. In addition, when the refrigerant R passes through theelectric motor 14, the oil A in the refrigerant R comes into contact with therotor 38 or anoil separation plate 38a which is provided on therotor 38 and extends in the radial direction, and thus, a content of the oil A in the refrigerant R decreases. - Meanwhile, the refrigerant R which has passed through the gap S between the
stator 39 and thehousing 11 does not come into contact with therotor 38 and flows toward thescroll compressor 13 as it is. Accordingly, the refrigerant R flows toward thescroll compressor 13 in a state where the content of the oil A in the refrigerant R is high. That is, the amount of the oil A in the refrigerant R discharged from therotary compressor 12 decreases on the radially inner side of thehousing 11 and increases on the radially outer side thereof. - Here, in the present embodiment, the
inflow restricting plate 61 having the restrictingsurface 62 is provided in the bearingcasing 31b, and thus, the flow of the refrigerant R to the suction opening FCa on the radially outer side can be restricted. Accordingly, it is possible to prevent the refrigerant R having a high content of oil A on the radially outer side flows into the suction channel FC through the suction opening FCa as it is. In addition, the refrigerant R on the radially inner side having a low content of oil A can flow into the suction channel FC through the suction opening FCa. - As a result, it is possible to supply the refrigerant R having a low content of oil A to the
scroll compressor 13, and it is possible to decrease the amount of the oil A in the refrigerant R which is compressed by thescroll compressor 13 and is discharged therefrom. It is possible to decrease an oil circulation amount (OC%) in a system including the two-stage compressor 1. - In addition, if the refrigerant R on the radially outer side comes into contact with the restricting
surface 62, the oil A in the refrigerant R is attached to the restrictingsurface 62, and the refrigerant R in which the content of the oil A has decreased is guided to the radially inner side by the restrictingsurface 62 and flows from suction opening FCa into suction channel FC. Accordingly, in a state where the amount of the oil A in the refrigerant R is decreased by the restrictingsurface 62, the refrigerant R is supplied from the suction channel FC to thescroll compressor 13. In this way, it is possible to decrease the amount of the oil A in the refrigerant R which is compressed by thescroll compressor 13 and is discharged from thedischarge pipe 34 to the outside of thehousing 11, and it is possible to decrease the oil circulation amount (OC%) in the system. - In addition, the
inflow restricting plate 61 is provided in the bearingcasing 31b, and thus, the restrictingsurface 62 can be provided in the bearingcasing 31b. Accordingly, compared to a case where a member corresponding to theinflow restricting plate 61 is attached to thehousing 11, a welding work or the like with respect to thehousing 11 is not required, and it is possible to very easily provide the restrictingsurface 62 in the bearingcasing 31b. Accordingly, it is possible to effectively separate the oil A in the refrigerant R from the refrigerant R while easily manufacturing the two-stage compressor 1 having the restrictingsurface 62. - In addition, the
oil return pipe 72 is provided, and thus, the oil which is used to lubricate the high stage-side compression section is returned into thehousing 11 through theoil return pipe 72. Accordingly, it is possible to further decrease the amount of the oil A in the refrigerant R which is compressed by thescroll compressor 13 and is discharged therefrom. In addition, theoil return pipe 72 is provided on the end portion on the radially outer side of the bearingcasing 31b, and thus, theoil return pipe 72 is provided at a position separated from the opening portion on the radially inner side in the suction opening FCa on the radially inner side. Therefore, the oil A which is returned from theoil return pipe 72 to thehousing 11 can be prevented from flowing from the suction opening FCa into the suction channel FC as it is. Accordingly, it is possible to further decrease the amount of the oil A in the refrigerant R which is compressed by thescroll compressor 13 and is discharged therefrom. - In addition, the refrigerant R having a high content of oil A which has passed through the gap S between the
housing 11 and thestator 39 in the region on the radially outer side inside thehousing 11 can be prevented from flowing from the portion between the restrictingsurface 62 and the inner surface of thehousing 11 into thescroll compressor 13 as it is by theseal member 66. Therefore, it is possible to further decrease the amount of the oil A in the refrigerant R which is compressed by thescroll compressor 13 and is discharged therefrom. - In addition, even when the recessed
portion 31c into which thewire 14a of theelectric motor 14 is inserted is formed in the bearingcasing 31b, it is possible to seal the gap among the recessedportion 31c, thewire 14a, and the inner surface of thehousing 11 by theseal member 65. Accordingly, it is possible to prevent the refrigerant R including the oil A from being supplied to thescroll compressor 13 through the gap as it is. - Next, a two-
stage compressor 80 according to a second embodiment of the present invention will be described with reference toFigs. 4 and5 . InFig. 4 , for convenience of descriptions, thewire 14a of theelectric motor 14 and theoil return pipe 72 are not shown. - The same reference numerals are assigned to the components similar to those of the second embodiment, and detail descriptions.
- In the two-
stage compressor 80 of the present embodiment, aninflow restricting plate 81 having a restrictingsurface 82 is different from theinflow restricting plate 61 of the first embodiment. - The
inflow restricting plate 81 includes anannular portion 83 which is disposed on the radially outer side along the inner surface of thehousing 11 and is formed in an annular shape about the axis X, and aconical portion 84 which is continuous to the radially inner side of theannular portion 83 so as to be provided integrally with theannular portion 83. - A lower surface of the
annular portion 83 is aflat surface 86 which is formed in an annular shape about the axis X. In addition, an outer surface of theconical portion 84 is aninclined surface 87 which is formed in a truncated conical shape about the axis X. Theinclined surface 87 is inclined downward from theflat surface 86 toward the radially inner side. - In this way, the restricting
surface 82 of the present embodiment includes theflat surface 86 and theinclined surface 87. Aninner edge portion 87a which is an end edge on the radially inner side of theinclined surface 87 is positioned on the radially inner side from thestator 39 and on the radially outer side from the bearingcasing 31b and therotary shaft 15. - In addition, in the present embodiment, the
inner edge portion 87a of theinflow restricting plate 81 is disposed at a position at which an intake amount of the refrigerant R required in thescroll compressor 13 can be secured, that is, an opening area of the suction opening FCa can be secured. - In the two-
stage compressor 80 of the above-described present embodiment, the restrictingsurface 82 has theinclined surface 87, and thus, it is possible to form an opening portion OP which is formed in an annular shape about the axis X so as to extend downward in the direction of the axis X from the suction opening FCa. Accordingly, compared to the first embodiment, the area of the suction opening FCa which is open toward theelectric motor 14 can increase. Therefore, it is possible to secure a flow rate of the refrigerant R flowing from the inside of thehousing 11 into the suction channel FC. - In addition, the refrigerant R having a high content of the oil A in the radially outer side region in the
housing 11 flows to the radially inner side along theflat surface 86, and thereafter, collides with theinclined surface 87, and thus, the oil A can be attached to theinclined surface 87. Accordingly, the refrigerant R can flow into the suction channel FC in a state where the content of the oil A in the refrigerant R further decreases so as to be supplied to thescroll compressor 13. As a result, it is possible to further decrease the amount of the oil A in the refrigerant R which is compressed by thescroll compressor 13 and is discharged to the outside of thehousing 11 and it is possible to further decrease the oil circulation amount (OC%) in the system including the two-stage compressor 80. - In addition, in the present embodiment, the
inner edge portion 87a on the radially inner side of theinclined surface 87 is positioned on the radially inner side from thestator 39, and thus, the restrictingsurface 82 extends to the position of therotor 38. Accordingly, the refrigerant R flowing through the radially inner side in thehousing 11 and the oil A in the refrigerant R come into contact with therotor 38, and the refrigerant R in which the amount of the oil A is sufficiently decreased by therotor 38 can flow from the suction opening FCa into the suction channel FC. - In addition, the
inner edge portion 87a of theinflow restricting plate 81 is disposed at the position at which the intake amount of the refrigerant R required in thescroll compressor 13 can be secured, and thus, it is possible to prevent compression efficiency in thescroll compressor 13 from decreasing. - Hereinbefore, the embodiments of the present invention are described in detail with reference to the drawings. However, the respective configurations and combinations thereof in the respective embodiments are merely examples, and additions, omissions, substations, and other modifications of configurations are possible within the scope which does not depart from the gist of the present invention. In addition, the present invention is not limited to the embodiments and are limited by only claims.
- For example, the bearing
casing 31b and each of theinflow restricting plates surfaces casing 31b. - In addition, similarly to the second embodiment, in the first embodiment, the
inner edge portion 62a of the restrictingsurface 62 may be disposed on the radially inner side from thestator 39. In addition, in this case, the position of theinner edge portion 62a may be determined such that the intake amount of the refrigerant R required in thescroll compressor 13 can be secured. - In addition, in the bearing
casing 31b, instead of the recessedportion 31c, a through-hole penetrating the bearingcasing 31b in the direction of the axis X may be formed such that thewire 14a is inserted into the through-hole so as to be disposed. - In addition, as shown in
Fig. 6 , an annular recessedportion 90 which is recessed upward and is formed in an annular shape about the axis X may be provided in the restrictingsurface 62A. According to the annular recessed portion, the refrigerant R on the radially outer side comes into contact with the restrictingsurface 62A, and thus, the oil A attached to the restrictingsurface 62A flows toward the radially inner side, and it is possible to prevent the oil A from being sucked into the suction opening FCa. The annular recessedportion 90 can be provided in any one of the restrictingsurface 62 of the first embodiment and the restrictingsurface 82 of the second embodiment. - In addition, in the
housing 11, therotary compressor 12 is provided as the low stage-side compressor and thescroll compressor 13 is provided as the high stage-side compressor. However, the present invention is not limited to this. For example, thescroll compressor 13 may be provided as the low stage-side compressor and therotary compressor 12 may be used as the high stage-side compressor. In addition, thescroll compressor 13 may be provided on both the low stage side and the high stage side, or therotary compressor 12 may be provided on both the low stage side and the high stage side. In addition, a compressor other than thescroll compressor 13 and therotary compressor 12 may be provided. - Moreover, the restricting
surfaces - According to the hermetic two-stage compressor, the hermetic two-stage compressor can be easily manufactured, and the oil in the gas can be effectively separated. Reference Signs List
-
- 1, 80: hermetic two-stage compressor
- 11: housing
- 12: rotary compressor (low stage-side compression section)
- 13: scroll compressor (high stage-side compression section)
- 14: electric motor
- 14a: wire
- 15: rotary shaft
- 21: main body portion
- 22: upper cover portion
- 23: lower cover portion
- 30: bearing device
- 31: upper bearing
- 31a: bearing
- 31b: bearing casing
- 31c: recessed portion (accommodation portion)
- 31d: bearing channel
- 32A, 32B: lower bearing
- 33: suction pipe
- 34: discharge pipe
- 37: through-hole
- 38: rotor
- 38a: oil separation plate
- 39: stator
- 41: eccentric shaft portion
- 42: piston rotor
- 44: cylinder
- 44a: suction hole
- 48: bolt
- 50: discharge cover
- 51: fixed scroll
- 52: end plate
- 52a: discharge hole
- 53: fixed lap
- 56: eccentric shaft portion
- 57: orbiting scroll
- 58: end plate
- 59: orbiting lap
- 60: bolt
- 61: inflow restricting plate
- 61a: notch
- 62, 62A: restricting surface
- 62a: inner edge portion
- 62b: outer edge portion
- 63: notch
- 65: seal member
- 66: seal member
- 72: oil return pipe (oil return section)
- 81: inflow restricting plate
- 82: restricting surface
- 83: annular portion
- 84: conical portion
- 86: flat surface
- 87: inclined surface
- 87a: inner edge portion
- 90: annular recessed portion
- C1: compression chamber
- C2: compression chamber
- 01: oil storage
- R: refrigerant
- X: axis
- A: oil
- S: gap
- FC: suction channel
- FCa: suction opening
- OP: opening portion
Claims (6)
- A hermetic two-stage compressor comprising:a housing which includes an oil storage inside the housing;a rotary shaft which is disposed in the housing;a motor which is disposed in the housing so as to rotate the rotary shaft and includes a stator which is provided on a radially outer side and a rotor which is provided on a radially inner side;a low stage-side compression section which is disposed on one side in an axial direction of the rotary shaft with respect to the motor in the housing and is connected to the rotary shaft so as to compress a gas;a bearing device which is disposed on the other side in the axial direction with respect to the motor in the housing and includes a bearing which supports the rotary shaft and a bearing casing which supports the bearing to the housing; anda high stage-side compression section which is disposed on the other side in the axial direction with respect to the bearing device and further compresses the gas discharged from the low stage-side compression section,wherein the bearing casing includesa suction channel which is provided to suck the gas into the high stage-side compression section and includes a suction opening which is open to the one side in the axial direction, anda restricting surface which is disposed between the suction opening and the motor and is provided toward the radially inner side from an inner surface of the housing so as to restrict a flow of the gas to the suction opening on the radially outer side.
- The hermetic two-stage compressor according to claim 1, further comprising:
an inflow restricting plate which is fixed to the bearing casing, is formed in a plate shape, and includes the restricting surface on the one side of the axial direction. - The hermetic two-stage compressor according to claim 1 or 2,
wherein the restricting surface includesa flat surface which is provided on an end portion on the radially outer side which is an inner surface side of the housing and is perpendicular to the axis to be formed in an annular shape about the axis, andan inclined surface which is inclined toward the one side in the axial direction from the flat surface toward the radially inner side so as to be formed in a truncated conical shape about the axis. - A hermetic two-stage compressor according to any one of claims 1 to 3,
wherein an inner edge portion on the radially inner side of the restricting surface is disposed at a position on the radially inner side of the stator, and
wherein the restricting surface closes a portion of the suction opening so as to secure an intake amount of the gas required in the high stage-side compression section. - The hermetic two-stage compressor according to any one of claims 1 to 4, further comprising:
a seal member which is provided in a gap between an outer edge portion on the radially outer side of the restricting surface and the inner surface of the housing. - The hermetic two-stage compressor according to any one of claims 1 to 5, further comprising:
an oil return section which is provided at a position of an end portion on the radially outer side in the bearing casing, and causes the high stage-side compression section and the one side in the axial direction from the bearing casing in the housing to communicate with each other such that oil from the high stage-side compression section can flow through the oil return section.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2016081000A JP6755114B2 (en) | 2016-04-14 | 2016-04-14 | Sealed two-stage compressor |
PCT/JP2017/015333 WO2017179714A1 (en) | 2016-04-14 | 2017-04-14 | Hermetic two-stage compressor |
Publications (3)
Publication Number | Publication Date |
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EP3409948A1 true EP3409948A1 (en) | 2018-12-05 |
EP3409948A4 EP3409948A4 (en) | 2019-03-06 |
EP3409948B1 EP3409948B1 (en) | 2020-05-13 |
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Application Number | Title | Priority Date | Filing Date |
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EP17782527.0A Active EP3409948B1 (en) | 2016-04-14 | 2017-04-14 | Hermetic two-stage compressor |
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EP (1) | EP3409948B1 (en) |
JP (1) | JP6755114B2 (en) |
KR (1) | KR102061440B1 (en) |
CN (1) | CN108700076B (en) |
AU (1) | AU2017251203B2 (en) |
WO (1) | WO2017179714A1 (en) |
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JP2023076187A (en) | 2021-11-22 | 2023-06-01 | 三菱重工サーマルシステムズ株式会社 | compressor |
JP2023076188A (en) | 2021-11-22 | 2023-06-01 | 三菱重工サーマルシステムズ株式会社 | compressor |
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US7044717B2 (en) * | 2002-06-11 | 2006-05-16 | Tecumseh Products Company | Lubrication of a hermetic carbon dioxide compressor |
JP2009047039A (en) * | 2007-08-17 | 2009-03-05 | Mitsubishi Heavy Ind Ltd | Multistage compressor |
US20090148328A1 (en) * | 2007-12-06 | 2009-06-11 | Chung-Hung Yeh | Lubricant backflow structure of compressor |
JP5444850B2 (en) * | 2009-05-27 | 2014-03-19 | ダイキン工業株式会社 | Compressor |
JP5709544B2 (en) * | 2011-01-17 | 2015-04-30 | 三菱重工業株式会社 | Compressor |
JP2012202252A (en) * | 2011-03-24 | 2012-10-22 | Sanyo Electric Co Ltd | Scroll compression device |
EP2960513B1 (en) * | 2011-07-22 | 2019-05-08 | Mitsubishi Heavy Industries Thermal Systems, Ltd. | Hermetic compressor |
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2016
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2017
- 2017-04-14 KR KR1020187025155A patent/KR102061440B1/en active IP Right Grant
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WO2017179714A1 (en) | 2017-10-19 |
AU2017251203B2 (en) | 2019-06-20 |
KR20180107215A (en) | 2018-10-01 |
KR102061440B1 (en) | 2019-12-31 |
JP2017190732A (en) | 2017-10-19 |
EP3409948B1 (en) | 2020-05-13 |
JP6755114B2 (en) | 2020-09-16 |
CN108700076A (en) | 2018-10-23 |
CN108700076B (en) | 2020-07-14 |
AU2017251203A1 (en) | 2018-08-30 |
EP3409948A4 (en) | 2019-03-06 |
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