WO2015111169A1 - 遠心圧縮機 - Google Patents
遠心圧縮機 Download PDFInfo
- Publication number
- WO2015111169A1 WO2015111169A1 PCT/JP2014/051401 JP2014051401W WO2015111169A1 WO 2015111169 A1 WO2015111169 A1 WO 2015111169A1 JP 2014051401 W JP2014051401 W JP 2014051401W WO 2015111169 A1 WO2015111169 A1 WO 2015111169A1
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- WO
- WIPO (PCT)
- Prior art keywords
- compression
- pressure
- space
- driven shaft
- unit
- Prior art date
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- 238000007906 compression Methods 0.000 claims abstract description 288
- 230000006835 compression Effects 0.000 claims abstract description 287
- 239000012530 fluid Substances 0.000 claims abstract description 89
- 238000006073 displacement reaction Methods 0.000 description 26
- 238000001816 cooling Methods 0.000 description 4
- 238000005259 measurement Methods 0.000 description 4
- 238000009434 installation Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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Classifications
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- 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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/051—Axial thrust balancing
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- 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
- F04D25/00—Pumping installations or systems
- F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
- F04D25/163—Combinations of two or more pumps ; Producing two or more separate gas flows driven by a common gearing arrangement
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- 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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/051—Axial thrust balancing
- F04D29/0516—Axial thrust balancing balancing pistons
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- 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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/053—Shafts
-
- 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
- F04D29/286—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors multi-stage rotors
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- 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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
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- 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
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
- F04D29/5826—Cooling at least part of the working fluid in a heat exchanger
Definitions
- the present invention relates to a centrifugal compressor.
- Centrifugal compressors include a single-shaft multi-stage centrifugal compressor with a structure in which an impeller that compresses gas such as gas is attached to a single shaft, and a built-in speed increaser with a structure in which impellers are attached to the shaft ends of multiple pinion shafts.
- a compressor hereinafter referred to as a geared compressor
- a geared compressor is known in which a fluid is compressed by a plurality of compression sections each provided with an impeller provided at each of shaft ends of a plurality of pinion shafts.
- Patent Document 1 discloses a double flow geared compressor in which a compression unit having the same configuration is provided at each end of each driven shaft that is a pinion shaft to which the rotation of the drive shaft is transmitted. Has been.
- This geared compressor rotates two compression parts with one driven shaft, and simultaneously compresses gas from both sides so that it becomes one compression part, without increasing the diameter of the impeller, the geared compressor The overall capacity is increased.
- the thrust force acting on the driven shaft from the compression portions at both ends is canceled, and the thrust force biased in either direction of the central axis is not applied to the driven shaft. It is preferable to do.
- the flow resistance may be different due to the difference in the length of the pipe connected to the discharge port of the compression unit. For this reason, a difference occurs between the discharge pressures of the compression portions on both sides, a thrust force is generated, and an unintended load may be applied to the driven shaft, the thrust bearing, and the like that support the compression portion.
- the present invention provides a centrifugal compressor capable of reducing a load caused by a difference in thrust force generated from two compression portions.
- a centrifugal compressor includes a drive shaft that is rotationally driven, a drive gear that is connected to the drive shaft, a driven gear that transmits the rotation of the drive gear, and the driven gear.
- a driven shaft extending to both sides in the central axis direction; a first compression portion that is provided on a first end side in the central axis direction of the driven shaft and compresses fluid by rotation of the driven shaft; and A second compression portion provided on the second end side in the central axis direction and compressing the fluid by rotation of the driven shaft; a pressure of a space on the fluid discharge side in the first compression portion; and the second compression portion And a pressure adjusting unit for uniformly adjusting the pressure of the space on the discharge side of the fluid.
- Such a centrifugal compressor can reduce the difference between the discharge pressure of the first compression section and the discharge pressure of the second compression section. Therefore, the thrust force generated by the pressure difference between the first compression portion and the second compression portion can be reduced. Thereby, the load which arises by the difference of the thrust force which arises from two compression parts of a 1st compression part and a 2nd compression part can be reduced.
- the centrifugal compressor according to the second aspect of the present invention includes a heat exchanger that performs heat exchange of fluid discharged from the first compression unit and the second compression unit, a discharge port of the first compression unit, and the A first connection path that connects a heat exchanger; and a second connection path that connects a discharge port of the second compression section and the heat exchanger; and the pressure adjustment section includes the first compression section.
- the first connection path and the second connection path may be connected at a position where the distance from the discharge port is equal to the distance from the discharge port of the second compression unit.
- the pressure in the space in the path can be made uniform.
- the difference in the length of the first connection path and the second connection path will cause a difference in pressure loss in the first connection path and the second connection path.
- the thrust force generated by the pressure difference between the first compression part and the second compression part can be easily reduced.
- the load by the difference of the thrust force which arises from two compression parts of a 1st compression part and a 2nd compression part can be reduced easily.
- the first compression section is fixed to the driven shaft, rotates with the driven shaft, and compresses the fluid.
- the first impeller A first casing that forms a first space with a surface on the second end side in the central axis direction of the driven shaft, and the second compression portion is fixed to the driven shaft.
- a second space that forms a second space between a second impeller that rotates together with the driven shaft and compresses fluid and a surface of the second impeller on the first end side in the central axis direction of the driven shaft.
- the pressure adjusting unit may be provided through the first casing and the second casing so as to communicate the first space and the second space.
- the pressure in the first space and the pressure in the second space can be made uniform. Therefore, the pressure difference can be reduced by making the pressure of the flow path on the suction port side closer to the discharge port in the first compression unit and the second compression unit. That is, the pressure in the flow path space on the fluid discharge side in the first compression section and the pressure in the flow path space on the fluid discharge side in the second compression section can be made close to each other with high accuracy. As a result, the difference generated between the discharge pressure of the first compression section and the discharge pressure of the second compression section can be further reduced. Therefore, by connecting the first space and the second space with the pressure adjusting unit, the thrust force generated by the pressure difference between the first compressing unit and the second compressing unit can be more easily reduced. Thereby, the load by the difference of the thrust force which arises from two compression parts of a 1st compression part and a 2nd compression part can be reduced further.
- the centrifugal compressor according to the fourth aspect of the present invention is characterized in that the pressure of the discharge side space of the first compression unit and the pressure of the discharge side space of the second compression unit, which are uniformly adjusted by the pressure adjustment unit, May be provided with a differential pressure adjusting unit for adjusting the pressure to a predetermined differential pressure.
- the difference between the pressure in the first space and the pressure in the second space can be adjusted from a uniform state, and can be adjusted to a predetermined differential pressure with high accuracy. Therefore, the thrust force acting on the driven shaft can be easily adjusted by the first compression portion and the second compression portion. Therefore, it is possible to cancel out the thrust force acting on the driven shaft, the drive shaft and the like other than the influence of the first compression portion and the second compression portion. As a result, stable operation can be performed without applying an extra load to the driven shaft or the drive shaft.
- the drive gear and the driven gear are helical gears
- the differential pressure adjusting unit cancels a thrust force generated by the drive gear and the driven gear. You may adjust so that it may become the differential pressure
- the driven shaft and the drive shaft by the helical gear are configured by setting the differential pressure to cancel the thrust force generated by the drive gear and the driven gear configured by the helical gear.
- the thrust force that worked on can be offset. Thereby, it can drive
- the pressure of the space on the discharge side of the fluid in the first compression section and the pressure of the space on the discharge side of the fluid in the second compression section are adjusted uniformly, so that the two compression sections It is possible to reduce the load caused by the deviation of the thrust force.
- the centrifugal compressor 1 of the present embodiment is a so-called geared compressor in which a speed increaser 10 is built.
- the centrifugal compressor 1 of the first embodiment includes a drive source 19 that generates power, a drive shaft 2 that is rotationally driven by the drive source 19, a speed increaser 10 that shifts and transmits the rotational drive of the drive shaft 2,
- the driven shaft 3 that outputs the power transmitted by the speed increaser 10, the plurality of compression units 4 that are driven by the power transmitted to the driven shaft 3, and the heat that cools the fluid compressed by the plurality of compression units 4
- the exchanger 5 and the piping part 6 which is a fluid flow path are provided.
- the drive shaft 2 is a rotation shaft that rotates around the central axis by the drive source 19.
- the speed increaser 10 includes a drive gear 11 connected on the second end side in the central axis direction of the drive shaft 2, a first driven gear 12 and a second driven gear 13 to which the rotation of the drive gear 11 is transmitted. And having.
- the speed increaser 10 includes a first intermediate gear 14 that transmits the rotation of the drive gear 11 to the first driven gear 12, and a second intermediate gear 15 that transmits the rotation of the drive gear 11 to the second driven gear 13. And have. That is, the gear group of the speed increaser 10 of this embodiment is arranged so as to mesh with the second intermediate gear 15, the drive gear 11, the first intermediate gear 14, and the first driven gear 12 in order from the second driven gear 13. Yes.
- a gear group constituting the speed increaser 10 is housed in the casing 20.
- the gear group constituting the speed increaser 10 in the present embodiment is a spur gear.
- the first intermediate gear 14 is rotatably supported by the first intermediate shaft 17.
- the second intermediate gear 15 is rotatably supported by the second intermediate shaft 18.
- the first intermediate shaft 17 and the second intermediate shaft 18 are supported on the casing 20 via a bearing (not shown).
- the driven shaft 3 has a first driven shaft 31 extending on both sides in the central axis direction of the first driven gear 12 and a second driven shaft 32 extending on both sides in the central axis direction of the second driven gear 13.
- the first driven shaft 31 and the second driven shaft 32 are supported on the casing 20 via a bearing (not shown).
- the compression unit 4 compresses and discharges a fluid such as a gas sucked from the suction port toward the radially outer peripheral side through a flow path formed therein.
- the compression unit 4 includes a first compression unit 41 provided on the first end side in the central axis direction, which is the side on which the drive source 19 is provided on the first driven shaft 31, and the drive source 19 on the first driven shaft 31.
- a second compression portion 42 provided on the second end portion side in the central axis direction opposite to the side provided with the first, and a second compression portion 42 provided on the second end portion side in the central axis direction in the second driven shaft 32.
- a third compression part 43 and a fourth compression part 44 provided on the second driven shaft 32 on the first end side in the central axis direction.
- the first compression unit 41 is provided at an end on the first end side in the central axis direction of the first driven shaft 31, and fluid is transferred from the suction port to the discharge port on the radially outer side by the rotation of the first driven shaft 31. Compressed and distributed.
- the first compression unit 41 is the first-stage compression unit 4 in the centrifugal compressor 1.
- the first compression portion 41 of the present embodiment is fixed to the first driven shaft 31 and rotates together with the first driven shaft 31 to compress the fluid, and covers the first impeller 41a and the fluid of the first impeller 41a.
- a first casing 41b that forms a flow path.
- the second compression section 42 is provided at the end on the second end side in the central axis direction of the first driven shaft 31, and fluid is transferred from the suction port to the discharge port on the radially outer side by the rotation of the first driven shaft 31. Compressed and distributed. That is, the second compression portion 42 is disposed at the opposite end of the first compression portion 41 with the first driven shaft 31 interposed therebetween.
- the second compression unit 42 has the same configuration as the first compression unit 41, and compresses the fluid having the same flow rate as the first compression unit 41 by the rotation of the first driven shaft 31.
- the second compression section 42 is the first compression section 4 in the centrifugal compressor 1 by compressing the fluid simultaneously with the first compression section 41.
- the second compression portion 42 of the present embodiment is fixed to the first driven shaft 31 and rotates together with the first driven shaft 31 to compress the fluid, and the second impeller 42a covers the second impeller 42a. And a second casing 42b that forms a flow path.
- the third compression portion 43 is provided at the end portion on the second end side in the central axis direction of the second driven shaft 32, and fluid is transferred from the suction port to the discharge port on the radially outer side by the rotation of the second driven shaft 32. Compressed and distributed.
- the third compression unit 43 is the second-stage compression unit 4 in the centrifugal compressor 1.
- the third compression portion 43 of the present embodiment is fixed to the second driven shaft 32, rotates with the second driven shaft 32, compresses the fluid, and covers the third impeller 43a to cover the fluid. And a third casing 43b that forms a flow path.
- the fourth compression unit 44 is provided at an end portion on the second end side in the central axis direction of the second driven shaft 32, and fluid is transferred from the suction port to the discharge port on the radially outer side by the rotation of the second driven shaft 32. Compressed and distributed. That is, the fourth compression portion 44 is disposed at the opposite end of the third compression portion 43 with the second driven shaft 32 interposed therebetween.
- the fourth compression unit 44 is the third-stage compression unit 4 in the centrifugal compressor 1.
- the fourth compression portion 44 of the present embodiment is fixed to the second driven shaft 32, rotates with the second driven shaft 32, compresses the fluid, and covers the fourth impeller 44a. And a fourth casing 44b that forms a flow path.
- the heat exchanger 5 reduces the power required for driving the centrifugal compressor 1 by intermediately cooling the fluid in the compression process.
- the heat exchanger 5 of the present embodiment includes a first heat exchanger 51 that performs cooling by exchanging heat of the fluid compressed by the first compression unit 41 and the second compression unit 42, and a third compression unit 43. And a second heat exchanger 52 for cooling the compressed fluid.
- the first heat exchanger 51 includes two inlet nozzles and one outlet nozzle.
- the first stage heat exchanger 5 cools the two systems of fluid discharged from the first compressor 41 and the second compressor 42 and joins the two systems of fluid.
- the first heat exchanger 51 is disposed between the first compression unit 41, the second compression unit 42, and the third compression unit 43.
- the first heat exchanger 51 of the present embodiment is disposed on the second end side in the central axis direction of the drive shaft 2, which is a position closer to the second compression part 42 than the first compression part 41.
- the second heat exchanger 52 includes one inlet nozzle and one outlet nozzle.
- the second stage heat exchanger 5 cools the fluid discharged from the third compression unit 43 and sends it to the fourth compression unit 44.
- the piping part 6 is a pipe that forms a flow path through which the fluid compressed by each compression part 4 flows.
- the piping part 6 includes a first compression part discharge pipe 61 that connects the first compression part 41 to the first heat exchanger 51, and a second compression part that connects the second compression part 42 to the first heat exchanger 51. It has a discharge pipe 62 and a third compression section suction pipe 63 that connects the first heat exchanger 51 to the third compression section 43.
- the piping part 6 includes a third compression part discharge pipe 64 that connects the third compression part 43 to the second heat exchanger 52, and a fourth compression part that connects the second heat exchanger 52 to the fourth compression part 44.
- the piping unit 6 includes a pressure adjusting unit 7 for uniformly adjusting the pressure at the discharge port of the first compression unit 41 and the pressure at the discharge port of the second compression unit 42.
- the first compression section discharge pipe 61 is a first connection path connecting the discharge port of the first compression section 41 and the first heat exchanger 51, and the fluid compressed by the first compression section 41 is subjected to the first heat. Distribute to the exchanger 51.
- the first compression section discharge pipe 61 connects the discharge port of the first compression section 41 and one of the inlet nozzles of the first heat exchanger 51.
- the 2nd compression part discharge piping 62 is the 2nd connection way which connects the discharge port of the 2nd compression part 42, and the 1st heat exchanger 51, Comprising: The fluid compressed by the 2nd compression part 42 is made into the 1st heat. Distribute to the exchanger 51.
- the second compression section discharge pipe 62 connects the discharge port of the second compression section 42 and one of the inlet nozzles on the side where the first compression section discharge pipe 61 of the first heat exchanger 51 is not connected. Yes.
- the third compression section suction pipe 63 is a pipe that joins the fluid from the first compression section 41 and the fluid from the second compression section 42 that are cooled by the first heat exchanger 51 to the third compression section 43. And the outlet nozzle of the 1st heat exchanger 51 and the suction inlet of the 3rd compression part 43 are connected.
- the third compression section discharge pipe 64 is a flow path for flowing the fluid compressed by the third compression section 43 to the second heat exchanger 52, and the discharge port of the third compression section 43 and the second heat exchanger 52. Is connected to the inlet nozzle.
- the fourth compression section suction pipe 65 is a pipe through which the fluid from the third compression section 43 cooled by the second heat exchanger 52 flows to the fourth compression section 44, and is an outlet nozzle of the second heat exchanger 52. To the suction port of the fourth compression portion 44.
- the fourth compression section discharge pipe 66 is a pipe that circulates the fluid compressed by the fourth compression section 44 to a predetermined plant P that is a supply destination of the compressed fluid, from the discharge port of the fourth compression section 44. It is connected to equipment (not shown) of the plant P.
- the pressure adjusting unit 7 uniformly adjusts the pressure in the discharge side space of the first compression unit 41 and the pressure in the discharge side space of the second compression unit 42.
- a first compression section discharge pipe 61 that is a first connection path and a second compression section discharge pipe 62 that is a second connection path are connected.
- the pressure adjusting unit 7 includes a distance l from the discharge port of the first compression unit 41 in the first compression unit discharge pipe 61 and a distance from the discharge port of the second compression unit 42 in the second compression unit discharge pipe 62. Communicate at a position where l is the same.
- the centrifugal compressor 1 according to the first embodiment having the above-described configuration.
- the centrifugal compressor 1 of the embodiment as described above when the fluid to be compressed is simultaneously sucked into the suction ports of the first compression unit 41 and the second compression unit 42, respectively, the first compression unit 41 and the second compression unit 42 are used.
- the first-stage compression is performed by
- the first compression section discharge pipe 61 and the second compression section discharge pipe 62 are the pressure adjustment section 7 at a position where the distances l from the discharge ports of the first compression section 41 and the second compression section 42 are the same. Connected by some piping. Therefore, the pressure in the vicinity of the pressure adjustment unit 7 in the first compression section discharge pipe 61 and the pressure in the vicinity of the pressure adjustment section 7 in the second compression section discharge pipe 62 are made uniform. . That is, the pressure in the space in the first compression section discharge pipe 61 that is the space on the fluid discharge side in the first compression section 41 and the second compression section discharge pipe that is the space on the fluid discharge side in the second compression section 42. The pressure in the space in 62 is almost uniform at the portion where the pressure adjusting unit 7 is connected.
- the state where the pressure is uniform means a state where the first compression portion 41 side and the second compression portion 42 side can be regarded as having substantially no influence on the first driven shaft 31 and the like.
- the fluid compressed by the first compressor 41 flows through the first compressor discharge pipe 61 and flows into the inlet nozzle of the first heat exchanger 51.
- the fluid compressed by the second compression section 42 flows through the second compression section discharge pipe 62 and flows into the inlet nozzle of the first heat exchanger 51.
- the fluid that has flowed into the two inlet nozzles of the first heat exchanger 51 from the first compression section discharge pipe 61 and the second compression section discharge pipe 62 is merged in the first heat exchanger 51 and subjected to intermediate cooling. Thereafter, when the gas flows through the third compression portion suction pipe 63 and flows into the suction port of the third compression portion 43, the second compression is performed by the third compression portion 43.
- the fluid compressed by the third compression unit 43 flows through the third compression unit discharge pipe 64 and flows into the second heat exchanger 52.
- the fluid that has flowed into the second heat exchanger 52 is intercooled in the second heat exchanger 52, then flows through the fourth compression section suction pipe 65 and flows into the suction port of the fourth compression section 44. Thereafter, the fluid is subjected to third-stage compression in the fourth compression unit 44 and then supplied to equipment of a predetermined plant P that is a supply destination of the compressed fluid.
- the pressure adjusting unit 7 makes the pressure on the discharge side of the fluid in the first compression unit 41 and the second compression unit 42 uniform so that the discharge pressure of the first compression unit 41 is increased. And the discharge pressure of the second compression unit 42 can be reduced. Therefore, the thrust force generated by the pressure difference between the first compression part 41 and the second compression part 42 can be reduced. Thereby, the load which arises by the difference of the thrust force which arises from the two compression parts 4 of the 1st compression part 41 and the 2nd compression part 42 can be reduced.
- first compression section discharge pipe 61 and the second compression section discharge pipe 62 are arranged at the same distance l from the discharge port of the first compression section 41 and the second compression section 42 by the pipe that is the pressure adjusting section 7. Is connected. Therefore, the pressure in the space in the first compression portion discharge pipe 61 that is connected to the discharge port of the first compression portion 41 and is the space on the discharge side of the fluid in the first compression portion 41, and the discharge port of the second compression portion 42 And the pressure in the space in the second compression section discharge pipe 62, which is the space on the fluid discharge side in the second compression section 42, can be made uniform.
- the pressure loss in the two pipes will be reduced. There will be a difference. That is, in this case, a difference occurs between the pressure in the first compression section discharge pipe 61 and the pressure in the second compression section discharge pipe 62, and the discharge pressure of the first compression section 41 and the discharge pressure of the second compression section 42 are There will be a difference.
- the discharge pressure of the first compression section 41 and the second compression section are equalized because the pressure in the space at the same position where the distances l from the discharge ports of the first compression section 41 and the second compression section 42 are equal is equal.
- the difference in the discharge pressure of 42 can be easily reduced. Therefore, the thrust force generated by the pressure difference between the first compression part 41 and the second compression part 42 can be easily reduced. Thereby, the load which arises by the difference of the thrust force which arises from the two compression parts 4 of the 1st compression part 41 and the 2nd compression part 42 can be reduced easily.
- centrifugal compressor 1 of the second embodiment will be described with reference to FIG.
- symbol is attached
- the centrifugal compressor 1 of the second embodiment is different from the first embodiment with respect to the position to which the pressure adjusting unit 7 is connected.
- the centrifugal compressor 1 according to the second embodiment is formed between the first impeller 41a of the first compressor 41 and the first casing 41b in place of the pressure adjuster 7, as shown in FIG. And a space pressure adjusting unit that connects the space and a space formed between the second impeller a of the second compression unit and the second casing b.
- the first casing A1 is formed so as to form a first space A1 between the first impeller 41a and the surface on the second end side in the central axis direction of the first driven shaft 31.
- 41b is arranged.
- the first space A1 is a space in the first casing 41b, and is a space defined by the first impeller 41a and the wall surface of the first casing 41b.
- the first space A1 is a space sandwiched between the bottom surface of the first impeller 41a on the second end side in the central axis direction of the first driven shaft 31 of the disk and the bottom of the first casing 41b.
- the second casing 42b is formed so as to form a second space A2 between the surface of the second impeller 42a and the first end shaft side in the central axis direction of the first driven shaft 31. Is arranged.
- the second space A2 is a space in the second casing 42b, and is a space defined by the second impeller 42a and the wall surface of the second casing 42b.
- the second space A2 is a space sandwiched between the bottom surface on the first end side in the central axis direction of the first driven shaft 31 of the disk of the second impeller 42a and the bottom portion of the second casing 42b.
- the space pressure adjusting unit 70 is provided through the first casing 41b and the second casing 42b so as to communicate the first space A1 and the second space A2.
- the space pressure adjusting unit 70 of the present embodiment has a first through hole 71 that penetrates the bottom surface of the first casing 41b that is a surface on the second end side in the central axis direction of the first driven shaft 31 in the first casing 41b.
- a second through hole 72 penetrating the bottom surface of the second casing 42b, which is a surface on the first end side in the central axis direction of the first driven shaft 31 in the second casing 42b, the first through hole 71 and the first It has a space pressure adjusting unit main body 73 that is a pipe having a small diameter of about 5 mm that connects the two through holes 72.
- the fluid sucked from the suction port of the first compression unit 41 is compressed by the rotation of the first impeller 41a. Then, the fluid flows toward the discharge port of the first compression unit 41. Since the first impeller 41a rotates with respect to the first casing 41b, a minute gap is formed between the first casing 41b and the first impeller 41a so as not to inhibit the flow of fluid.
- the first space A1 communicates with the flow path on the fluid discharge side through this minute gap. Therefore, the pressure in the first space A1 is substantially equal to the pressure corresponding to the discharge-side flow path through which the compressed fluid flows.
- the fluid sucked from the suction port of the second compression section 42 is compressed by the rotation of the second impeller 42a. Then, the fluid flows toward the discharge port of the second compressor. Since the second impeller 42a rotates relative to the second casing 42b, a minute gap is formed between the second casing 42b and the second impeller 42a so as not to inhibit the flow of fluid.
- the second space A2 communicates with the flow path on the fluid discharge side through this minute gap. Therefore, the pressure in the second space A2 is substantially equal to the pressure corresponding to the discharge-side flow path through which the compressed fluid flows.
- the pressure in the first space A1 and the second space A2 are communicated.
- the pressure with the space A2 is uniform. That is, the fluid pressure in the flow path on the discharge side of the fluid in the first compression section 41 communicating with the first space A1 with a minute gap and the fluid in the second compression section 42 communicating with the second space A2 with a minute gap.
- the pressure in the space in the flow path on the discharge side is almost constant.
- the fluid compressed by the first compression unit 41 flows through the first compression unit discharge pipe 61 and flows into the inlet nozzle of the first heat exchanger 51.
- the fluid compressed by the second compression section 42 flows through the second compression section discharge pipe 62 and flows into the inlet nozzle of the first heat exchanger 51.
- the centrifugal compressor 1 As described above, the first space A ⁇ b> 1 and the second space A ⁇ b> 2 are connected via the first through hole 71 and the second through hole 72 by the pipe that is the space pressure adjusting unit main body 73.
- the pressure in the first space A1 and the pressure in the second space A2 can be made uniform. Therefore, the pressure difference can be reduced by making the pressure in the flow path closer to the suction port than the discharge port in the first compression unit 41 and the second compression unit 42 become uniform.
- the pressure in the flow path space on the fluid discharge side in the first compression section 41 and the pressure in the flow path space on the fluid discharge side in the second compression section 42 can be made close to each other with high accuracy.
- the difference generated between the discharge pressure of the first compression unit 41 and the discharge pressure of the second compression unit 42 can be further reduced. Therefore, by connecting the first space A1 and the second space A2 with the space pressure adjusting portion main body 73, the thrust force generated by the pressure difference between the first compression portion 41 and the second compression portion 42 can be further reduced. Can do. Thereby, the load by the difference of the thrust force which arises from the two compression parts 4 of the 1st compression part 41 and the 2nd compression part 42 can be reduced further.
- first space A1 and the second space A2 are spaces facing the first casing 41b and the second casing 42b, respectively, only the first through hole 71 and the second through hole 72 are provided in each casing 20.
- the space pressure adjusting unit 70 that connects the first space A1 and the second space A2 can be provided.
- centrifugal compressor 1 of the third embodiment will be described with reference to FIG.
- symbol is attached
- the centrifugal compressor 1 of the third embodiment is different from the first embodiment in that a difference is caused again in the pressure made uniform by the pressure adjusting unit 7.
- the centrifugal compressor 1 of the third embodiment has a differential pressure adjusting unit 8 provided in the spatial pressure adjusting unit 70 of the second embodiment as shown in FIG.
- the gear group of the speed increaser 10 of the centrifugal compressor 1 of the present embodiment is constituted by a helical gear. That is, the drive gear 11a, the first driven gear 12a, the second driven gear 13a, the first intermediate gear 14a, and the second intermediate gear 15a are all helical gears.
- the differential pressure adjusting unit 8 has a predetermined pressure difference between the pressure on the discharge side of the first compression unit 41 and the pressure on the discharge side of the second compression unit 42, which is uniformly adjusted by the space pressure adjusting unit 70. Adjust to achieve differential pressure.
- the differential pressure adjusting unit 8 according to the present embodiment is configured so that the pressure in the first space A1 and the pressure in the second space A2 are made uniform by the space pressure adjusting unit 70 according to the thrust force generated in the first driven shaft 31. Adjust to make a difference.
- the differential pressure adjusting unit 8 calculates a predetermined differential pressure based on the displacement measuring unit 81 that measures the displacement of the first driven shaft 31 in the central axis direction and the measured displacement of the first driven shaft 31.
- a valve unit 83 that adjusts the opening amount of the space pressure adjustment unit main body 73 based on the calculation result of the differential pressure control unit 82.
- the displacement measuring unit 81 measures a relative displacement amount of the first driven shaft 31 in the central axis direction with respect to the casing 20 by a displacement sensor installed in the casing 20.
- the displacement measuring unit 81 outputs the measurement result to the differential pressure control unit 82.
- the differential pressure control unit 82 includes a displacement input unit 82a to which the measurement result of the displacement measurement unit 81 is input, a thrust force calculation unit 82b that calculates a thrust force acting on the first driven shaft 31 based on the input displacement, Based on the thrust force calculated by the thrust force calculation unit 82b, a differential pressure calculation unit 82c that calculates a differential pressure in the first space A1 and the second space A2, and a valve unit based on the calculation result of the differential pressure calculation unit 82c 83 has a valve adjusting portion 82d for instructing the opening amount.
- the displacement input unit 82 a receives information on the relative displacement amount in the central axis direction of the first driven shaft 31 with respect to the casing 20 measured by the displacement measuring unit 81.
- the displacement input unit 82a sends information on the input relative displacement amount to the thrust force calculation unit 82b.
- the thrust force calculator 82b calculates how much thrust force is acting on the first driven shaft 31 based on the received information on the relative displacement amount.
- the thrust force calculation unit 82b sends the calculated thrust force to the differential pressure calculation unit 82c.
- the differential pressure calculation unit 82c Based on the received thrust force, the differential pressure calculation unit 82c generates a thrust force on the first driven shaft 31 by the first driven gear 12a connected to the drive gear 11a of the speed increaser 10 via the first intermediate gear 14a. The pressure difference between the pressure in the first space A1 and the pressure in the second space A2 is calculated so as to cancel out the above.
- the differential pressure calculation unit 82c sends information to the valve adjustment unit 82d with the calculated differential pressure as a predetermined differential pressure.
- the valve adjustment unit 82d calculates the opening amount of the valve unit 83 based on the received information on the predetermined differential pressure, and sends an instruction to the valve unit 83 as a signal so that the calculated opening amount is obtained.
- the valve part 83 is provided in the middle of the piping which is the space pressure adjusting part main body 73.
- the valve unit 83 adjusts the flow rate of the pipe by opening and closing the valve based on the signal input from the valve adjustment unit 82d.
- the centrifugal compressor 1 of the third embodiment having the above configuration.
- the gear group constituting the speed increaser 10 is formed of a helical gear
- the rotation of the drive shaft 2 is transmitted and the first intermediate gear 14a and A thrust force acts on one of the first driven gear 12a and the like in the central axis direction. That is, a thrust force is exerted on the first driven shaft 31 connected to the first driven gear 12a in either direction of the central axis.
- the first driven shaft 31 moves to the first end side or the second end side in the central axis direction with respect to the casing 20.
- a displacement measuring unit 81 provided in the casing 20 measures a relative displacement amount in the central axis direction with respect to the casing 20.
- the displacement measuring unit 81 outputs information on the measured relative displacement amount to the displacement input unit 82 a of the differential pressure control unit 82.
- the displacement input unit 82a to which the information on the relative displacement amount is input sends the input information to the thrust force calculation unit 82b.
- the thrust force calculation unit 82b calculates the thrust force acting on the first driven shaft 31 by the gear group of the gearbox 10 based on the received displacement amount information.
- the thrust force calculation unit 82b sends information on the calculated thrust force to the differential pressure calculation unit 82c.
- the differential pressure calculation unit 82c based on the received thrust force information, the pressure in the first space A1 and the pressure in the second space A2, which are differential pressures for canceling the thrust force acting on the first driven shaft 31. Is calculated as a predetermined differential pressure.
- the differential pressure calculation unit 82c sends information on the calculated predetermined differential pressure to the valve adjustment unit 82d.
- the valve adjustment unit 82d Based on the received information on the predetermined differential pressure, the valve adjustment unit 82d calculates the opening amount of the valve unit 83 and sends an instruction to the valve unit 83 as a signal.
- the valve unit 83 adjusts the amount of communication of the piping that is the space pressure adjusting unit main body 73 so that the instructed opening amount is obtained. As a result, the pressure between the first space A1 and the second space A2 is shifted by a predetermined differential pressure.
- the fluid compressed by the first compressor 41 flows through the first compressor discharge pipe 61 and flows into the inlet nozzle of the first heat exchanger 51.
- the fluid compressed by the second compression section 42 flows through the second compression section discharge pipe 62 and flows into the inlet nozzle of the first heat exchanger 51.
- the first driven shaft 31 moves toward the smaller thrust force in the central axis direction. Therefore, the first driven shaft 31 is returned to the position before the first driven shaft 31 is moved by the thrust force acting from the gearbox 10 constituted by a helical gear while the rotation of the drive shaft 2 is transmitted.
- the pressure in the first space A1 and the pressure in the second space A2 that can be uniformly adjusted by the space pressure adjusting unit 70 are calculated by the differential pressure calculating unit 82c.
- the opening amount of the valve portion 83 is adjusted so that the differential pressure becomes the same.
- the difference between the pressure in the first space A1 and the pressure in the second space A2 can be adjusted from a uniform state, and can be adjusted to a predetermined differential pressure with high accuracy. Therefore, the thrust force acting on the first driven shaft 31 by the first compression part 41 and the second compression part 42 can be easily adjusted.
- the thrust force acting on the first driven shaft 31 and the drive shaft 2 connected to the first driven shaft 31 other than the influence of the first compression portion 41 and the second compression portion 42 can be easily canceled.
- the first driven shaft 31 and the drive shaft 2 that are the speed increaser 10 can be stably operated without applying an extra load.
- the gear group such as the drive gear 11a and the first driven gear 12a is a helical gear
- the predetermined differential pressure calculated by the differential pressure calculation unit 82c is canceled out by the thrust force generated by these gear groups.
- the thrust force acting on the first driven shaft 31 and the drive shaft 2 connected to the first driven shaft 31 by the helical gear can be offset.
- the first driven shaft 31 and the drive shaft 2 can be operated more stably without applying an extra load.
- the compression unit 4 is not limited to a three-stage configuration like the centrifugal compressor 1 of the present embodiment. That is, a two-stage configuration without the fourth compression unit 44 may be employed, or a fifth or sixth compression unit may be provided and a four-stage or more configuration may be employed.
- the pressure of the space on the discharge side of the fluid in the first compression section and the pressure of the space on the discharge side of the fluid in the second compression section are adjusted uniformly, so that the two compression sections It is possible to reduce the load caused by the deviation of the thrust force.
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Abstract
Description
以下、本発明における第一実施形態について図1及び図2を参照して説明する。
図1に示すように、本実施形態の遠心圧縮機1は、増速機10を内蔵したいわゆるギアド圧縮機である。第一実施形態の遠心圧縮機1は、動力を発生させる駆動源19と、駆動源19によって回転駆動される駆動軸2と、駆動軸2の回転駆動を変速、伝達させる増速機10と、増速機10によって伝達された動力が出力される従動軸3と、従動軸3に伝達された動力により駆動する複数の圧縮部4と、複数の圧縮部4で圧縮された流体を冷却する熱交換器5と、流体の流路である配管部6とを備える。
増速機10は、駆動軸2の中心軸方向の第二の端部側で接続される駆動歯車11と、駆動歯車11の回転がそれぞれ伝達される第一従動歯車12及び第二従動歯車13と、を有する。増速機10は、第一従動歯車12に対して駆動歯車11の回転を伝達する第一中間歯車14と、第二従動歯車13に対して駆動歯車11の回転を伝達する第二中間歯車15とを有する。即ち、本実施形態の増速機10の歯車群は、第二従動歯車13から順に第二中間歯車15、駆動歯車11、第一中間歯車14、第一従動歯車12と互いに噛み合って配置されている。増速機10を構成する歯車群は、ケーシング20の内部に収められている。本実施形態における増速機10を構成する歯車群は、平歯車である。
上記のような実施形態の遠心圧縮機1では、圧縮すべき流体が第一圧縮部41及び第二圧縮部42の吸込口にそれぞれ同時に吸い込まれると、第一圧縮部41及び第二圧縮部42によって一段目の圧縮が行われる。
なお、ここでいう圧力が均一な状態とは、第一圧縮部41側と第二圧縮部42側とで実質的に第一従動軸31等に影響を及ぼさないとみなせる程度の差しかない状態をいう。
次に、図3を参照して第二実施形態の遠心圧縮機1について説明する。
第二実施形態においては第一実施形態と共通の構成要素には同一の符号を付して詳細な説明を省略する。この第二実施形態の遠心圧縮機1は、圧力調整部7の接続される位置について、第一実施形態と相違する。
第一空間A1は、第一ケーシング41b内の空間であって、第一インペラ41aと第一ケーシング41bの壁面とによって画成される空間である。第一空間A1は、第一インペラ41aのディスクの第一従動軸31の中心軸方向の第二の端部側の底面と、第一ケーシング41bの底部とによって挟まれた空間である。
第二空間A2は、第二ケーシング42b内の空間であって、第二インペラ42aと第二ケーシング42bの壁面とによって画成される空間である。第二空間A2は、第二インペラ42aのディスクの第一従動軸31の中心軸方向の第一の端部側の底面と、第二ケーシング42bの底部とによって挟まれた空間である。
第一圧縮部41の吸込口から吸い込まれた流体は、第一インペラ41aが回転することで圧縮される。そして、第一圧縮部41の吐出口に向かって流体は流れていく。第一インペラ41aは第一ケーシング41bに対して回転するために、第一ケーシング41bと第一インペラ41aとの間には流体の流れを阻害しないような微小な隙間が形成されている。第一空間A1はこの微小な隙間によって流体の吐出側の流路と連通している。そのため、第一空間A1内の圧力は、圧縮された流体が流通する吐出側の流路に対応する圧力とほぼ同等となっている。
次に、図4を参照して第三実施形態の遠心圧縮機1について説明する。
第三実施形態においては第一実施形態と共通の構成要素には同一の符号を付して詳細な説明を省略する。この第三実施形態の遠心圧縮機1は、圧力調整部7によって均一にされた圧力に再び差を生じさせる点について、第一実施形態と相違する。
差圧制御部82は、変位測定部81の測定結果が入力される変位入力部82aと、入力された変位に基づいて第一従動軸31に働くスラスト力を算出するスラスト力算出部82bと、スラスト力算出部82bで算出したスラスト力に基づいて、第一空間A1と第二空間A2とにおける差圧を算出する差圧算出部82cと、差圧算出部82cの算出結果に基づいて弁部83に開放量を指示する弁調整部82dとを有する。
スラスト力算出部82bは、受け取った相対変位量の情報に基づいて、第一従動軸31にどれだけのスラスト力が働いているかを算出する。スラスト力算出部82bは、算出したスラスト力を差圧算出部82cに送る。
弁調整部82dは、受け取った所定の差圧の情報に基づいて、弁部83の開放量を算出し、算出した開放量となるように弁部83に指示を信号として送る。
第三実施形態の遠心圧縮機1は、増速機10を構成する歯車群がはすば歯車で形成されているため、駆動軸2の回転が伝達される中で、第一中間歯車14aや第一従動歯車12a等に中心軸方向のいずれか一方に向かってスラスト力が働く。即ち、第一従動歯車12aと接続されている第一従動軸31にも中心軸方向のいずれか一方に向かってスラスト力が働く。その結果、第一従動軸31は、ケーシング20に対して中心軸方向の第一の端部側か第二の端部側のいずれかに移動する。
19 駆動源
2 駆動軸
10 増速機
11、11a 駆動歯車
12、12a 第一従動歯車
13、13a 第二従動歯車
14、14a 第一中間歯車
15、156a 第二中間歯車
17 第一中間軸
18 第二中間軸
20 ケーシング
3 従動軸
31 第一従動軸
32 第二従動軸
4 圧縮部
41 第一圧縮部
41a 第一インペラ
41b 第一ケーシング
42 第二圧縮部
42a 第二インペラ
42b 第二ケーシング
43 第三圧縮部
43a 第三インペラ
43b 第三ケーシング
44 第四圧縮部
44a 第四インペラ
44b 第四ケーシング
5 熱交換器
51 第一熱交換器
52 第二熱交換器
6 配管部
61 第一圧縮部吐出配管
62 第二圧縮部吐出配管
63 第三圧縮部吸込配管
64 第三圧縮部吐出配管
65 第四圧縮部吸込配管
66 第四圧縮部吐出配管
7 圧力調整部
l (吐出口からの)距離
70 空間圧力調整部
71 第一貫通孔
72 第二貫通孔
73 空間圧力調整部本体
A1 第一空間
A2 第二空間
8 差圧調整部
81 変位測定部
82 差圧制御部
82a 変位入力部
82b スラスト力算出部
82c 差圧算出部
82d 弁調整部
83 弁部
P プラント
Claims (5)
- 回転駆動される駆動軸と、
前記駆動軸に接続される駆動歯車と、
前記駆動歯車の回転が伝達される従動歯車と、
前記従動歯車の中心軸方向の両端側へと延びる従動軸と、
前記従動軸の中心軸方向の第一の端部側に設けられ、前記従動軸の回転によって流体を圧縮する第一圧縮部と、
前記従動軸の中心軸方向の第二の端部側に設けられ、前記従動軸の回転によって流体を圧縮する第二圧縮部と、
前記第一圧縮部における流体の吐出側の空間の圧力と前記第二圧縮部における流体の吐出側の空間の圧力とを均一に調整するための圧力調整部とを備える遠心圧縮機。 - 前記第一圧縮部及び前記第二圧縮部から吐出される流体の熱交換を行う熱交換器と、
前記第一圧縮部の吐出口と前記熱交換器とを接続する第一接続路と、
前記第二圧縮部の吐出口と前記熱交換器とを接続する第二接続路と、を備え、
前記圧力調整部は、前記第一圧縮部の吐出口からの距離と、前記第二圧縮部の吐出口からの距離とが同じとなる位置で、前記第一接続路と前記第二接続路とを接続する請求項1に記載の遠心圧縮機。 - 前記第一圧縮部は、
前記従動軸に対して固定されて該従動軸とともに回転して流体を圧縮する第一インペラと、前記第一インペラの前記従動軸の中心軸方向の第二の端部側の面との間に第一空間を形成する第一ケーシングとを有し、
前記第二圧縮部は、
前記従動軸に対して固定されて該従動軸とともに回転して流体を圧縮する第二インペラと、前記第二インペラの前記従動軸の中心軸方向の第一の端部側の面との間に第二空間を形成する第二ケーシングとを有し、
前記圧力調整部は、前記第一空間及び前記第二空間を連通させるように、前記第一ケーシング及び前記第二ケーシングを貫通して設けられる請求項1または請求項2に記載の遠心圧縮機。 - 前記圧力調整部によって均一に調整された前記第一圧縮部の吐出側の空間の圧力と前記第二圧縮部の吐出側の空間の圧力とを、所定の差圧となるよう調整する差圧調整部を備える請求項1から請求項3のいずれか一項に記載の遠心圧縮機。
- 前記駆動歯車及び前記従動歯車がはすば歯車であり、
前記差圧調整部は、前記駆動歯車と前記従動歯車とによって生じるスラスト力を相殺する差圧となるよう調整する請求項4に記載の遠心圧縮機。
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CN201480030156.2A CN105264233B (zh) | 2014-01-23 | 2014-01-23 | 离心压缩机 |
EP14880032.9A EP2990654B1 (en) | 2014-01-23 | 2014-01-23 | Centrifugal compressor |
PCT/JP2014/051401 WO2015111169A1 (ja) | 2014-01-23 | 2014-01-23 | 遠心圧縮機 |
US14/893,320 US10145381B2 (en) | 2014-01-23 | 2014-01-23 | Geared centrifugal compressor with pressure adjustment portion to balance axial thrust |
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- 2014-01-23 WO PCT/JP2014/051401 patent/WO2015111169A1/ja active Application Filing
- 2014-01-23 CN CN201480030156.2A patent/CN105264233B/zh not_active Expired - Fee Related
- 2014-01-23 EP EP14880032.9A patent/EP2990654B1/en not_active Not-in-force
- 2014-01-23 JP JP2015558648A patent/JP6120997B2/ja active Active
- 2014-01-23 US US14/893,320 patent/US10145381B2/en active Active
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Cited By (2)
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JP2016223433A (ja) * | 2015-06-01 | 2016-12-28 | 株式会社Ihi | 遠心圧縮機、及び回転機械 |
CN108779777A (zh) * | 2016-03-08 | 2018-11-09 | 流体处理有限责任公司 | 在多级泵中平衡轴向力的中心衬套 |
Also Published As
Publication number | Publication date |
---|---|
JPWO2015111169A1 (ja) | 2017-03-23 |
CN105264233B (zh) | 2017-10-27 |
US10145381B2 (en) | 2018-12-04 |
EP2990654B1 (en) | 2018-01-10 |
EP2990654A4 (en) | 2016-06-08 |
CN105264233A (zh) | 2016-01-20 |
US20160131155A1 (en) | 2016-05-12 |
JP6120997B2 (ja) | 2017-04-26 |
EP2990654A1 (en) | 2016-03-02 |
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