US20170167501A1 - Impeller and centrifugal compressor - Google Patents

Impeller and centrifugal compressor Download PDF

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Publication number
US20170167501A1
US20170167501A1 US15/039,312 US201415039312A US2017167501A1 US 20170167501 A1 US20170167501 A1 US 20170167501A1 US 201415039312 A US201415039312 A US 201415039312A US 2017167501 A1 US2017167501 A1 US 2017167501A1
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US
United States
Prior art keywords
hole
impeller
blade
radial direction
disk
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
US15/039,312
Other languages
English (en)
Inventor
Ryosuke Saito
Shinji Iwamoto
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
Mitsubishi Heavy Industries Compressor Corp
Original Assignee
Mitsubishi Heavy Industries Ltd
Mitsubishi Heavy Industries Compressor Corp
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, Mitsubishi Heavy Industries Compressor Corp filed Critical Mitsubishi Heavy Industries Ltd
Assigned to MITSUBISHI HEAVY INDUSTRIES, LTD., MITSUBISHI HEAVY INDUSTRIES COMPRESSOR CORPORATION reassignment MITSUBISHI HEAVY INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: IWAMOTO, SHINJI, SAITO, RYOSUKE
Publication of US20170167501A1 publication Critical patent/US20170167501A1/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
    • F04D29/26—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
    • 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
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage 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
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage 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
    • F04D29/284—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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F04D29/682—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid extraction
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F04D29/684—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid injection

Definitions

  • the present invention relates to an impeller and a centrifugal compressor.
  • PTL 1 discloses that cross bleed holes penetrating both surface of a shroudless blade are provided on the shroudless blade which is used in a fan of a compressor or an axial flow gas turbine.
  • the cross bleed holes are provided in the vicinity of a tip of the blade.
  • the present invention is made to solve the above-described problem and is to provide an impeller in which energy loss decreases and efficiency increases.
  • an impeller including: a disk which rotates around an axis; and a plurality of blades which are provided at intervals therebetween in a circumferential direction on one side surface in an axial direction of the disk, and demarcate a channel through which a fluid flowing in from the one side in the axial direction is discharged toward the outside in a radial direction, in which a hole is formed in the blade, and the hole communicates with a pressure surface facing a front side in a rotational direction and a suction surface facing a rear side in the rotational direction.
  • a portion of the fluid flowing into the inner portion of the channel is injected to the inner portion of the channel of the suction surface side as a jet stream via the hole. It is possible to dissipate a secondary flow and a swirl generated in the suction surface side of the blade by the jet stream.
  • the hole may extend toward a downstream side of the channel as the hole is directed from the pressure surface side to the suction surface side.
  • a plurality of holes may be arranged so as to be separated from each other from the inside in the radial direction of a duct toward the outside in the radial direction.
  • an opening area of the hole may increase from the pressure surface side toward the suction surface side.
  • the opening area of the hole may decrease from the pressure surface side toward the suction surface side.
  • the hole may have a groove which is spirally formed on an inner peripheral surface of the hole.
  • the hole may have one inflow port which is provided on the pressure surface side, and may have a plurality of injection ports which communicate with the inflow port and are provided on the suction surface side.
  • the jet stream is injected to a wider region on the suction surface side, and it is possible to more effectively dissipate the secondary flow and the swirl generated on the suction surface side.
  • centrifugal compressor including the impeller according to any one of the first to seventh aspects.
  • the impeller of the present invention it is possible to provide an impeller in which energy loss decreases and efficiency increases.
  • FIG. 1 is a sectional view showing an outline of a centrifugal compressor according to the present invention.
  • FIG. 2 is a circumferential sectional view of an impeller according to a first embodiment of the present invention.
  • FIG. 3 is a sectional view taken along line A-A of FIG. 1 in a blade according to the first embodiment of the present invention.
  • FIG. 4 is a view showing a region in which a hole H according to each embodiment of the present invention is provided.
  • FIG. 5 is a sectional view of a blade according to a second embodiment of the present invention.
  • FIG. 6 is a sectional view showing a modification example of the blade according to the second embodiment of the present invention.
  • FIG. 7 is a sectional view of a blade according to a third embodiment of the present invention.
  • FIG. 8 is a sectional view showing a modification example of the blade according to the third embodiment of the present invention.
  • FIG. 9 is a sectional view of a blade according to a fourth embodiment of the present invention.
  • FIG. 10 is a sectional view of a blade according to a fifth embodiment of the present invention.
  • a centrifugal compressor 100 which is a rotary machine of the present embodiment is mainly configured of a shaft 102 which rotates around an axis O, impellers 1 which are attached to the shaft 102 and compress a process gas (gas) G using centrifugal force, and a casing 105 which rotatably supports the shaft 102 and in which a channel 104 through which the process gas G flows from an upstream side to a downstream side is formed.
  • the casing 105 is formed so as to have an approximately columnar outline and the shaft 102 is disposed so as to penetrate the center of the casing 105 .
  • Journal bearings 105 a are provided on both ends of the casing 105 in the axial direction of the shaft 102 , and a thrust bearing 105 b is provided on one end.
  • the journal bearings 105 a and the thrust bearing 105 b rotatably support the shaft 102 . That is, the shaft 102 is supported by the casing 105 via the journal bearings 105 a and the thrust bearing 105 b.
  • an intake port 105 c through which the process gas G flows in from the outside is provided on one end side of the casing 105 in the axial direction
  • an exhaust port 105 d through which the process gas G is discharged to the outside is provided on the other end side.
  • the internal space functions as a space for accommodating the impellers 1 and functions as the channel 104 .
  • the intake port 105 c and the exhaust port 105 d communicate with each other via the impellers 1 and the channel 104 .
  • the plurality of impellers 1 are arranged with intervals therebetween in the axial direction of the shaft 102 .
  • six impellers 1 are provided. However, at least one or more impeller may be provided.
  • the impeller 1 is configured so as to include a disk 2 and a plurality of blades 3 .
  • the disk 2 is formed in an approximately circular shape in a front view, and is rotatable around the shaft about the above-described axis O.
  • a disk surface 4 is curvedly formed from a predetermined position S on the inside in the radial direction slightly separated toward the outside in the radial direction from the axis O toward the outside in the radial direction.
  • the surface positioned on the inside in the radial direction is formed along the axis O, and is formed so as to be gradually concaved in the radial direction toward the outside in the radial direction.
  • the thickness of the disk 2 in the axial direction decreases from one (upstream side) of the end surfaces in the axial direction as the disk 2 is directed from the position S on the inside in the radial direction which is slightly separated from the axis O toward the outside in the radial direction, and a decrease amount in the thickness of the disk 2 in the axial direction becomes larger as the position of the thickness moves inward and the decrease amount becomes smaller as the position of the thickness moves outward.
  • the plurality of blades 3 are approximately radially disposed and are erected so as to be approximately perpendicular to the disk surface 4 .
  • the thickness of each of the blades 3 is approximately uniformly formed from an end portion of the blade of the disk surface 4 side to the end portion of the tip side opposite to the disk surface 4 side.
  • the blade 3 when the blade 3 is viewed from the direction of the axis O, the blade 3 has a shape which is curved so as to be a slightly convex surface in a rotational direction of the disk 2 from the end portion on the inside in the radial direction to the end portion on the outside in the radial direction.
  • the impeller 1 rotates, in blade surfaces of the concave surface side and the convex surface side of the curved blade 3 , the blade surface of the concave surface side which is the rear side of the convex surface becomes a suction surface n while the blade surface of the convex surface side becomes a pressure surface p.
  • FIG. 2 is a view showing a section taken along line A-A of FIG. 1 .
  • line A-A is a line which passes through an intermediate position in a height direction of the blade 3 based on the disk surface 4 .
  • a tip end t of the blade 3 is formed so as to be curved from the inside in the radial direction of the disk 2 to the outside in the radial direction. More specifically, similarly to the above-described disk surface 4 , the tip end is formed along the axis O as it is positioned on the inside in the radial direction, and the tip end is formed so as to be gradually concaved along the radial direction toward the outside in the radial direction.
  • the height of the blade 3 based on the disk surface 4 becomes high as the position of the height is positioned further on the inside in the radial direction of the disk 2 , and the height becomes low as the position of the height is positioned further on the outside in the radial direction.
  • an impeller channel 10 of the impeller 1 is configured of a shroud surface 5 which is configured by the casing 105 , the pressure surface p and the suction surface n of the blade 3 which are adjacent to each other, and the disk surface 4 between the pressure surface p and the suction surface n. That is, two impeller channels 10 and 10 are configured so as to be adjacent to each other via one blade 3 .
  • a hole H which penetrates the blade 3 from the pressure surface p toward the suction surface n is formed in the middle of the extension of the blade 3 .
  • the hole H is formed to penetrate the blade 3 so as to have a predetermined angle with respect to the thickness direction of the blade 3 .
  • a position of an inflow port H 1 on the pressure surface p side and a position of an injection port H 2 on the suction surface n side are formed so as to be deviated from each other when viewed in the circumferential direction of the disk 2 , and the inflow port H 1 and the injection port H 2 are formed so as to linearly communicate with each other. That is, the impeller channels 10 and 10 adjacent to each other via the blade 3 communicate with each other by the hole H.
  • the penetrating direction of the hole H is set so as to be approximately the same as a line which connects intermediate positions in the height direction of the blade 3 based on the disk surface 4 in the axial direction.
  • a sectional shape of the hole H when viewed in the penetrating direction of the hole H is circular.
  • an opening size of the hole H is approximately determined according to design.
  • the opening size of the inflow port H 1 of the hole H is the same as that of the injection port H 2 of the hole H.
  • the position at which the hole H (inflow port H 1 ) is provided will be described with reference to FIG. 4 . That is, the position at which the hole H is provided is inside a region A in FIG. 4 .
  • the region A is a region which is surrounded by a virtual curve L 1 along a flow direction of a fluid on the surface of the blade 3 , virtual curves L 2 and L 3 orthogonal to the virtual curve L 1 , and the disk surface 4 .
  • the virtual curve L 1 is curved along the flow direction of the fluid, and is set so as to pass through approximately 60% of the positions of the height from the disk surface 4 to the tip end t of the blade 3 .
  • the virtual curve L 2 is set so as to pass through approximately 20% of the positions of the dimension from an end edge of an inlet 6 side of the impeller channel 10 to an end edge of an outlet 7 side in the blade 3 .
  • the virtual curve L 3 is set so as to pass through approximately 60% of the positions of the dimension from the end edge of the inlet 6 side to the end edge of the outlet 7 side.
  • the region A is an approximately rectangular region which includes the pair of long sides formed arcuately and the pair of short sides connecting the long sides, and similarly to the disk surface 4 , the region A is formed along the axis O as it is positioned on the inside in the radial direction, and the region A is formed so as to be gradually concaved along the radial direction as it is directed the outside in the radial direction.
  • the height of the blade 3 based on the disk surface 4 becomes higher as the position of the height is positioned on the inside in the radial direction of the disk 2 , and the height becomes lower as the position of the height is positioned on the outside in the radial direction.
  • the injection port H 2 is also formed so as to be included inside the region A.
  • the tip end t side of the blade 3 is covered by the casing 105 (refer to FIG. 1 ), and the impeller channel 10 of the impeller 1 is configured of the shroud surface 5 which is configured by the casing 105 , the pressure surface p and the suction surface n of the blade 3 which are adjacent to each other, and the disk surface 4 between the pressure surface p and the suction surface n. Accordingly, by rotating the impeller 1 , a fluid flows in from the inlet 6 of the impeller channel 10 positioned on the inside in the radial direction of the disk 2 , and the fluid flows to the outside from the outlet 7 positioned on the outside in the radial direction by centrifugal force. That is, as shown in FIG.
  • the fluid forms a main stream F.
  • the main stream F follows the curved direction of the disk surface 4 .
  • the main stream F exists over the entire height direction of the blade 3 .
  • a representative direction of the main stream F is shown by one arrow.
  • the state of the main stream F in a case where the hole H is not provided in the blade 3 is described. That is, the flow direction is gradually changed from the axial direction to the radial direction as the impeller channel 10 is directed from the inside in the radial direction of the disk 2 to the outside in the radial direction, and as described above, the impeller channel 10 is curvedly formed from the inlet 6 toward the outlet 7 . Due to the impeller channel 10 being curvedly formed and centrifugal force toward the outside in the radial direction being generated according to the rotation of the impeller 1 , in the impeller channel 10 , a secondary flow F 2 shown by a dashed arrow in FIG. 2 is formed in addition to the main stream F.
  • the secondary flow F 2 reaches a region k of the shroud surface 5 side close to the suction surface n of a latter half portion 11 of the outlet 7 side of the impeller channel 10 , and forms a swirl. That is, the secondary flow F 2 stays in the region k as a fluid having low energy.
  • the hole H penetrating the blade 3 from the pressure surface p toward the suction surface n is formed in the middle of the extension of the blade 3 .
  • a portion of the fluid flowing in from the inlet 6 of the impeller channel flows into the hole H from the inflow port H 1 of the pressure surface p side, and is injected toward the adjacent impeller channel 10 (the impeller channel 10 positioned on the rear side in the rotational direction of the impeller 1 ) via the blade 3 from the injection port H 2 of the suction surface n.
  • the fluid injected from the injection port H 2 forms a jet stream FJ.
  • the hole H penetrates the blade 3 in the same direction as the extension direction of the line which connects the intermediate positions in the height direction of the blade 3 based on the disk surface 4 . That is, the direction of the hole H is approximately the same as the direction of the main stream F flowing in the vicinity of the hole H. Accordingly, the flow direction of the jet stream FJ injected from the hole H is approximately the same as the direction of the main stream F.
  • the jet stream FJ having approximately the same directional components as those of the main stream F collides with the secondary flow F 2 having directional components different from those of the flow direction of the main stream F.
  • an opening volume of the hole H is sufficiently smaller than a volume of the impeller channel 10 , the jet stream FJ passing through the hole H has a higher pressure than that of the vicinity of the jet stream FJ. In other words, the jet stream FJ has a higher flow rate than that of the secondary flow F 2 .
  • the secondary flow F 2 is deviated by the jet stream FJ, flows in approximately the same direction as that of the jet stream FJ, that is, in the approximately the same direction as that of the main stream F, and the directional components of the secondary flow F 2 directing the region k decrease.
  • the hole H which communicates with the pressure surface p facing the front side in the rotational direction and the suction surface n facing the rear side in the rotational direction, is formed in the blade 3 .
  • the swirl generated in the region k due to the secondary flow F 2 decreases by the jet stream FJ injected from the hole H, and components staying in the region k as a fluid having low energy decrease. That is, in the impeller 1 , pressure loss due to the secondary flow F 2 decreases, and it is possible to obtain high efficiency.
  • the hole H extends toward the downstream side of the impeller channel 10 as the hole is directed from the pressure surface p side toward the suction surface n side.
  • FIG. 5 is a view showing the blade 3 of the impeller 1 according to the present embodiment.
  • the opening area of the injection port H 2 provided on the suction surface n side is larger than the opening area of the inflow port H 1 provided on the pressure surface p side. That is, the hole H is formed such that the opening area increases from the pressure surface p side toward the suction surface n side.
  • the hole H may be formed such that opening area of the injection port H 2 provided on the suction surface n side is smaller than the opening area of the inflow port H 1 provided on the pressure surface p side. That is, the hole H may be formed such that the opening area decreases from the pressure surface p side toward the suction surface n side.
  • the plurality of holes H are provided so as to be separated from each other from the inside in the radial direction of the disk 2 toward the outside in the radial direction.
  • three holes H are shown.
  • the three holes H are approximately linearly arranged so as to be separated from the disk surface 4 from the hole H positioned on the inside in the radial direction toward the hole H positioned on the outside in the radial direction.
  • all three holes are formed inside the region A shown in FIG. 4 .
  • three holes H may be arranged along the height direction of the blade 3 based on the disk surface 4 .
  • the hole H has a spiral groove C on the inner peripheral surface of the hole H.
  • the groove C is formed so as to draw a circle along the inner peripheral surface of the hole H from the pressure surface p side toward the suction surface n side. That is, the groove C has a female screw shape.
  • the circumference direction of the groove C may be the clockwise direction or the counterclockwise direction.
  • the hole H includes one inflow port H 1 which is provided on the pressure surface p side and a plurality of injection ports H 2 which are provided on the suction surface n side.
  • FIG. 10 shows a configuration in which three injection ports H 2 are provided. Each of the three injection ports H 2 communicates with one inflow port H 1 .
  • the three injection ports H 2 are arranged so as to be separated from each other from the inside in the radial direction of the disk 2 toward the outside in the radial direction. That is, three channels are formed inside the hole H toward the injection ports H 2 with the inflow path H 1 as the starting point.
  • the channel which is positioned in the innermost side in the radial direction among the three channels linearly communicates with the inflow port H 1 .
  • the divided jet stream is injected from the three injection ports H 2 to the suction surface n side. Accordingly, it is possible to supply the jet stream FJ to the suction surface n side in a wide range. Moreover, since only one inflow port H 1 is provided on the pressure surface p side, the components of the flow extracted from the main stream F so as to form the jet stream FJ may decrease.
  • the opening shape of the hole H is circular.
  • the opening shape of the hole H is not limited to this, and may be a rectangular slit shape, or a polygon such as a triangular shape.
  • the opening shape may be an elliptical shape.
  • the impeller of the present invention it is possible to provide an impeller in which energy loss decreases and efficiency increases. It is possible to apply the impeller according to the present invention to a rotary machine such as a centrifugal compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US15/039,312 2014-01-22 2014-07-23 Impeller and centrifugal compressor Abandoned US20170167501A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2014009680A JP6249219B2 (ja) 2014-01-22 2014-01-22 インペラ及び遠心圧縮機
JP2014-009680 2014-01-22
PCT/JP2014/069451 WO2015111243A1 (ja) 2014-01-22 2014-07-23 インペラ及び遠心圧縮機

Publications (1)

Publication Number Publication Date
US20170167501A1 true US20170167501A1 (en) 2017-06-15

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US15/039,312 Abandoned US20170167501A1 (en) 2014-01-22 2014-07-23 Impeller and centrifugal compressor

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US (1) US20170167501A1 (enExample)
EP (1) EP3098454A4 (enExample)
JP (1) JP6249219B2 (enExample)
CN (1) CN105723096A (enExample)
WO (1) WO2015111243A1 (enExample)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US12180974B2 (en) 2022-03-24 2024-12-31 Copeland Lp Variable inlet guide vane apparatus and compressor including same
US12516678B2 (en) 2023-03-20 2026-01-06 Copeland Lp Variable inlet guide vane apparatus combined with compressor end cap

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB256647A (en) * 1925-08-08 1926-10-21 Gen Electric Improvements in or relating to centrifugal blowers and compressors
US2161182A (en) * 1937-01-22 1939-06-06 Alfred N Massey Supercharger for internal combustion engines
DE860898C (de) * 1944-02-29 1952-12-29 Aeg Laufrad fuer Kreiselpumpen
CH398320A (de) * 1961-06-27 1966-03-15 Sulzer Ag Kreiselpumpe
JPS53123506U (enExample) * 1977-03-07 1978-10-02
DE4214753A1 (de) * 1992-05-04 1993-11-11 Asea Brown Boveri Radialverdichter-Laufrad
JP3948785B2 (ja) * 1996-05-17 2007-07-25 カルソニックカンセイ株式会社 遠心多翼ファン
EP0807760B1 (en) * 1996-05-17 2003-09-17 Calsonic Kansei Corporation Centrifugal multiblade fan
US6860715B2 (en) * 2003-04-24 2005-03-01 Borgwarner Inc. Centrifugal compressor wheel
US7261513B2 (en) * 2004-12-01 2007-08-28 Kabushiki Kaisha Toyota Jidoshokki Centrifugal compressor
JP2006194238A (ja) * 2004-12-14 2006-07-27 Toyota Industries Corp 遠心圧縮機
GB0910838D0 (en) 2009-06-24 2009-08-05 Rolls Royce Plc A shroudless blade
JP2012052439A (ja) * 2010-08-31 2012-03-15 Mitsubishi Heavy Ind Ltd インペラ
CN202326441U (zh) * 2011-12-02 2012-07-11 杭州求是透平机制造有限公司 一种用于离心压缩机叶片扩压器的楔形叶片

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US12180974B2 (en) 2022-03-24 2024-12-31 Copeland Lp Variable inlet guide vane apparatus and compressor including same
US12516678B2 (en) 2023-03-20 2026-01-06 Copeland Lp Variable inlet guide vane apparatus combined with compressor end cap

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Publication number Publication date
CN105723096A (zh) 2016-06-29
JP2015137592A (ja) 2015-07-30
JP6249219B2 (ja) 2017-12-20
EP3098454A1 (en) 2016-11-30
EP3098454A4 (en) 2017-08-16
WO2015111243A1 (ja) 2015-07-30

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