WO2022172885A1 - 電動遠心圧縮機 - Google Patents
電動遠心圧縮機 Download PDFInfo
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- WO2022172885A1 WO2022172885A1 PCT/JP2022/004662 JP2022004662W WO2022172885A1 WO 2022172885 A1 WO2022172885 A1 WO 2022172885A1 JP 2022004662 W JP2022004662 W JP 2022004662W WO 2022172885 A1 WO2022172885 A1 WO 2022172885A1
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- Prior art keywords
- pressure stage
- bearing
- impeller
- centrifugal compressor
- gap
- Prior art date
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- 239000000314 lubricant Substances 0.000 claims abstract description 25
- 238000010926 purge Methods 0.000 claims description 53
- 230000002093 peripheral effect Effects 0.000 claims description 41
- 238000007789 sealing Methods 0.000 claims description 10
- 238000005096 rolling process Methods 0.000 claims description 7
- 238000007599 discharging Methods 0.000 claims description 4
- 239000007787 solid Substances 0.000 abstract 1
- 239000007789 gas Substances 0.000 description 77
- 239000004519 grease Substances 0.000 description 29
- 239000000446 fuel Substances 0.000 description 14
- 239000003595 mist Substances 0.000 description 8
- 230000014509 gene expression Effects 0.000 description 5
- 239000000203 mixture Substances 0.000 description 5
- 230000006866 deterioration Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000006870 function Effects 0.000 description 4
- 238000011144 upstream manufacturing Methods 0.000 description 4
- 238000001816 cooling Methods 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000000567 combustion gas Substances 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000001737 promoting effect Effects 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
- 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
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/02—Surge control
-
- 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
- F04D29/056—Bearings
-
- 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
- F04D29/056—Bearings
- F04D29/059—Roller bearings
-
- 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
- F04D29/08—Sealings
- F04D29/10—Shaft sealings
- F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
- F04D29/104—Shaft sealings especially adapted for elastic fluid pumps the sealing fluid being other than the working fluid or being the working fluid treated
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/067—Fixing them in a housing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/42—Pumps with cylinders or pistons
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/30—Hydrogen technology
- Y02E60/50—Fuel cells
Definitions
- the present disclosure relates to electric centrifugal compressors.
- This application claims priority based on Japanese Patent Application No. 2021-020356 filed with the Japan Patent Office on February 12, 2021, the content of which is incorporated herein.
- An electric centrifugal compressor is sometimes installed in a fuel cell vehicle that generates electricity with a fuel cell mounted on the vehicle body and runs on the power of an electric motor.
- the electric centrifugal compressor supplies compressed air to the fuel cell to improve the efficiency of the fuel cell.
- an object of at least one embodiment of the present disclosure is to provide an electric centrifugal compressor in which parts around the bearing can be simplified.
- An electric centrifugal compressor includes: an electric motor including a rotating shaft; a first impeller provided on one end side of the rotating shaft; a first bearing rotatably supporting the rotating shaft at a position between the first impeller and the electric motor and containing a lubricant; a first bearing housing that houses the first bearing; with The first bearing housing includes a compressed gas supply hole for supplying compressed gas from the outside of the first bearing housing to a gap between the rotating body including the rotating shaft and the first bearing housing, The outlet of the compressed gas supply hole is provided on the inner surface of the first bearing housing and positioned between the first impeller and the first bearing in the axial direction of the rotating shaft.
- an electric centrifugal compressor capable of simplifying parts around the bearing.
- FIG. 1 It is a sectional view showing roughly composition of electric centrifugal compressor 1 concerning one embodiment of this indication. 1. It is a figure which shows the cross section in which the position of the circumferential direction differs from the cross section shown in FIG. 1 about the electric centrifugal compressor 1 shown in FIG. 3 is an enlarged view of the vicinity of a high-pressure stage sleeve 18B in the cross section shown in FIG. 2; FIG. FIG. 4 is a diagram schematically showing an AA section of FIG. 3; FIG. 3 is an enlarged view of the vicinity of a low-pressure stage sleeve 18A in the cross section shown in FIG. 2; FIG.
- FIG. 2 is an enlarged view of the vicinity of a high-pressure stage side sleeve 18B of the electric centrifugal compressor 1 according to one embodiment, schematically showing a cross section along the rotation axis CA of the electric centrifugal compressor 1.
- FIG. FIG. 7 is a schematic cross-sectional view showing a state in which the rotational speed of the rotary shaft 3 in the electric centrifugal compressor 1 shown in FIG. 6 has exceeded a reference value;
- FIG. 2 is an enlarged view of the vicinity of a high-pressure stage side sleeve 18B of the electric centrifugal compressor 1 according to one embodiment, and schematically shows a cross section along the rotation axis CA of the electric centrifugal compressor 1.
- FIG. 9 is a schematic cross-sectional view showing a state in which the rotational speed of the rotary shaft 3 in the electric centrifugal compressor 1 shown in FIG. 8 exceeds a reference value; 2 is a cross-sectional view schematically showing the configuration of an electric centrifugal compressor 1 including a negative pressure pump 230.
- expressions that express shapes such as squares and cylinders do not only represent shapes such as squares and cylinders in a geometrically strict sense, but also include irregularities and chamfers to the extent that the same effect can be obtained.
- the shape including the part etc. shall also be represented.
- the expressions “comprising”, “including”, or “having” one component are not exclusive expressions excluding the presence of other components.
- symbol may be attached
- FIG. 1 is a schematic configuration diagram schematically showing the configuration of an electric centrifugal compressor 1 according to an embodiment of the present disclosure.
- the electric centrifugal compressor 1 is schematically shown in cross section along the rotation axis CA of the rotary shaft 3 .
- An electric centrifugal compressor 1 according to some embodiments of the present disclosure, as shown in FIG. A multi-stage electric centrifugal compressor configured to be driven by
- An exemplary electric centrifugal compressor 1 shown in FIG. A side bearing 15B, a low-pressure stage bearing housing 16A, and a high-pressure stage bearing housing 16B are provided.
- the direction in which the rotation axis CA of the rotating shaft 3 extends is defined as the axial direction X
- the direction perpendicular to the rotation axis CA is defined as the radial direction Y.
- the side where the low-pressure stage impeller 4 is located with respect to the high-pressure stage impeller 5 (right side in FIG. 1) is the low-pressure stage side XL
- the side opposite to the low-pressure stage side XL (left side in FIG. 1) is the high pressure stage side. Let it be XH on the stage side.
- An electric motor 10 mounted in the electric centrifugal compressor 1 includes a rotating body 11 as a rotor, a motor stator 12 as a stator, and a stator housing 17 configured to accommodate the motor stator 12 .
- Rotating body 11 includes rotating shaft 3 and rotor assembly 13 attached to the outer circumference of rotating shaft 3 .
- Rotor assembly 13 includes permanent magnets 14 .
- the motor stator 12 is arranged to surround the outer periphery of the rotor assembly 13 and is supported by the stator housing 17 inside the stator housing 17 .
- the motor stator 12 includes a motor coil (stator coil) 121 and is configured to generate a magnetic field that rotates the rotor 11 on which the permanent magnets 14 are mounted by power supplied from a power source (not shown).
- a motor coil stator coil
- the impellers the low-pressure stage impeller 4 and the high-pressure stage impeller 5 attached to the rotating shaft 3 interlock and rotate. do.
- the electric centrifugal compressor 1 rotates the low-pressure stage impeller 4 to compress the gas introduced into the low-pressure stage housing 6 and pressurize the gas to the first pressure. Compressed gas pressurized to the first pressure is led into the high pressure stage housing 7 through the connecting pipe 8 . The electric centrifugal compressor 1 rotates the high-pressure stage impeller 5 to further compress the compressed gas introduced into the high-pressure stage housing 7 to a second pressure higher than the first pressure. pressurize.
- the low-pressure stage housing 6 has, as shown in FIG. of low pressure stage outlet openings 62 are formed. Inside the low-pressure stage housing 6 , there are provided a supply passage 63 for guiding the gas introduced into the low-pressure stage housing 6 from the low-pressure stage inlet opening 61 to the low-pressure stage impeller 4 , and the gas passing through the low-pressure stage impeller 4 . and a scroll channel 64 leading to the low pressure stage outlet opening 62 is formed.
- the low pressure stage inlet opening 61 opens towards the low pressure stage side XL in the axial direction X.
- the low-pressure stage outlet opening 62 opens in a direction that intersects (for example, orthogonally) the rotation axis CA.
- the low-pressure stage impeller 4 is provided on one end side of the rotary shaft 3 .
- the low-pressure stage impeller 4 has a hub 41 mechanically connected to one end side of the rotating shaft 3 and a plurality of impeller blades 43 provided on the outer peripheral surface of the hub 41 .
- the low-pressure stage impeller 4 is rotatable integrally with the rotating shaft 3 around the rotation axis CA of the rotating shaft 3 .
- the low-pressure stage impeller 4 is a centrifugal impeller configured to direct the gas sent along the axial direction X from the low-pressure stage side XL to the outside in the radial direction Y.
- a gap (clearance) is formed between each tip of the plurality of impeller blades 43 and the convexly curved shroud surface of the low-pressure stage housing 6 .
- the low-pressure stage housing 6 is combined with another member (low-pressure stage side bearing housing 16A in the illustrated example) to form a low-pressure stage impeller chamber that rotatably accommodates the low-pressure stage impeller 4.
- 66 is formed.
- the low-pressure stage impeller chamber 66 communicates with the supply channel 63 located upstream in the gas flow direction and the scroll channel 64 located downstream in the gas flow direction.
- the scroll flow path 64 has a spiral shape surrounding the outer side in the radial direction Y of the low-pressure stage impeller 4 .
- Gas (for example, air) guided from the outside of the low-pressure stage housing 6 to the supply flow path 63 through the low-pressure stage inlet opening 61 is sent to the low-pressure stage impeller 4 after flowing through the supply flow path 63 to the high-pressure stage side XH. is compressed by the rotation of the low-pressure stage impeller 4 and pressurized to the first pressure. Compressed gas (compressed air, for example) that has passed through the low-pressure stage impeller 4 flows outward in the radial direction Y through the scroll passage 64 , and is then discharged from the low-pressure stage outlet opening 62 to the outside of the low-pressure stage housing 6 .
- Compressed gas compressed air, for example
- the high pressure stage housing 7 has, as shown in FIG. of high pressure stage outlet openings 72 are formed. Inside the high-pressure stage housing 7, there are provided a supply passage 73 for guiding the gas introduced into the inside of the high-pressure stage housing 7 from the high-pressure stage inlet opening 71 to the high-pressure stage impeller 5, and a scroll channel 74 leading to the high pressure stage outlet opening 72 is formed.
- each of the high pressure stage inlet opening 71 and the high pressure stage outlet opening 72 opens in a direction that intersects (eg, is perpendicular to) the axis of rotation CA.
- the high-pressure stage impeller 5 is provided on the other end side of the rotating shaft 3 .
- the high-pressure stage impeller 5 has a hub 51 mechanically connected to the other end side of the rotating shaft 3 and a plurality of impeller blades 53 provided on the outer peripheral surface of the hub 51 .
- the high-pressure stage impeller 5 is rotatable integrally with the rotating shaft 3 around the rotation axis CA of the rotating shaft 3 .
- the high-pressure stage impeller 5 is a centrifugal impeller configured to guide the gas sent along the axial direction X from the high-pressure stage side XH to the outside in the radial direction Y.
- a gap (clearance) is formed between each tip of the plurality of impeller blades 53 and the convexly curved shroud surface of the high-pressure stage housing 7 .
- the high pressure stage housing 7 is combined with another member (the high pressure stage side bearing housing 16B in the illustrated example) to form a high pressure stage impeller chamber that rotatably accommodates the high pressure stage impeller 5.
- 76 is formed.
- the high-pressure stage impeller chamber 76 communicates with the supply channel 73 located upstream in the gas flow direction and the scroll channel 74 located downstream in the gas flow direction.
- the scroll flow path 74 has a spiral shape surrounding the outer side of the high-pressure stage impeller 5 in the radial direction Y. As shown in FIG.
- the electric centrifugal compressor 1 includes a connecting pipe 8 for supplying compressed gas compressed by the low-pressure stage impeller 4 to the high-pressure stage housing 7 .
- the connecting pipe 8 is formed in a tubular shape extending along its length direction, and includes a high pressure stage side connection portion 81 connected to the high pressure stage inlet opening 71 and a low pressure stage outlet. and a low voltage stage side connection portion 82 connected to the opening 62 .
- each of the high-pressure stage-side connection portion 81 and the low-pressure stage-side connection portion 82 extends along a direction that intersects (perpendicularly in the illustrated example) the rotation axis CA of the rotary shaft 3 .
- the connecting pipe 8 includes an intermediate portion 83 extending along the rotation axis CA of the rotating shaft, a low-pressure stage-side curved portion 84 having a curved shape connecting the low-pressure stage-side connection portion 82 and the intermediate portion 83, and a high-pressure stage-side A high-pressure stage side curved portion 85 having a curved shape connecting the connection portion 81 and the intermediate portion 83 is further included.
- the boundaries of each portion of the connecting pipe 8 are indicated by two-dot chain lines.
- Each part of the connecting pipe 8 may be composed of separate members, or may be integrally formed from a single material.
- the compressed gas discharged from the low-pressure-stage outlet opening 62 of the low-pressure-stage housing 6 flows through the connecting pipe 8 from the low-pressure-stage-side connection portion 82 toward the high-pressure-stage-side connection portion 81 , and then flows through the high-pressure-stage inlet of the high-pressure-stage housing 7 . It is led to a supply channel 73 through the opening 71 .
- the compressed gas guided to the supply flow path 73 is sent to the high-pressure stage impeller 5, compressed by the rotation of the high-pressure stage impeller 5, and pressurized to a second pressure higher than the first pressure.
- the compressed gas that has passed through the high-pressure stage impeller 5 flows outward in the radial direction Y through the scroll passage 74 , and then is discharged from the high-pressure stage housing 7 through the high-pressure stage outlet opening 72 .
- the electric centrifugal compressor 1 is an electric centrifugal compressor for fuel cell vehicles. Therefore, the compressed gas compressed by the high-pressure stage impeller 5 is supplied to the air electrode of the fuel cell (not shown).
- the present disclosure may be applied to electric centrifugal compressors other than those for fuel cell vehicles, for example electric centrifugal compressors for internal combustion engines that pressurize combustion gas sent to an internal combustion engine such as an engine.
- the high-pressure stage housing 7 has a high-pressure stage inlet opening 71 in a direction intersecting with the rotation axis CA of the rotary shaft 3 , and the connecting pipe 8 is connected to the high-pressure stage inlet opening 71 .
- a high-pressure stage side connection portion 81 is connected. Therefore, the compressed gas compressed by the low-pressure stage impeller 4 is supplied to the inside of the high-pressure stage housing 7 from the outer peripheral side (outside in the radial direction Y) of the high-pressure stage housing 7 through the connecting pipe 8 .
- the length of the connecting pipe 8 and the high pressure stage housing 7 in the axial direction X is shortened.
- the length of the electric centrifugal compressor 1 in the axial direction X can be shortened, so that the size and weight of the multi-stage electric centrifugal compressor can be reduced.
- the electric centrifugal compressor 1 a high pressure ratio can be achieved at a low flow rate, and a multi-stage electric centrifugal compressor excellent in thrust load balance can be realized.
- the low-pressure stage bearing 15A rotatably supports the rotating shaft 3 at a position between the low-pressure stage impeller 4 and the electric motor 10 (between the low-pressure stage impeller 4 and the rotor assembly 13).
- the low-pressure stage side bearing 15A is a grease-filled ball bearing in which grease is pre-filled as a lubricant. Ball bearings do not require idling, do not require a complicated system, have good marketability, and are excellent in durability against repeated rotation and stoppage of the rotating shaft 3, as compared with air bearings.
- the high-pressure stage bearing 15B rotatably supports the rotary shaft 3 at a position between the high-pressure stage impeller 5 and the electric motor 10 (between the high-pressure stage impeller 5 and the rotor assembly 13).
- the high-pressure stage side bearing 15B is composed of a grease-filled ball bearing in which grease is pre-filled as a lubricant.
- the structure of the parts around the low-pressure stage side bearing 15A (for example, the low-pressure stage side bearing housing 16A) can be simplified. As a result, it is possible to reduce the size and weight of the multistage electric centrifugal compressor.
- the high-pressure stage side bearing 15B since it is not necessary to supply grease to the high-pressure stage side bearing 15B, it is possible to simplify the structure of the parts around the high-pressure stage side bearing 15B (for example, the high-pressure stage side bearing housing 16B). It is possible to reduce the size and weight of the machine.
- the low-pressure stage-side bearing housing 16A accommodates the low-pressure stage-side bearing 15A, and the low-pressure stage-side bearing 15A is supported by a bearing support surface 161 formed inside the low-pressure stage-side bearing housing 16A.
- the high pressure stage bearing housing 16B accommodates the high pressure stage bearing 15B, and the high pressure stage bearing 15B is supported by a bearing support surface 162 formed inside the high pressure stage bearing housing 16B.
- the low-pressure stage bearing housing 16A, the high-pressure stage bearing housing 16B, and the stator housing 17 are arranged between the low-pressure stage housing 6 and the high-pressure stage housing 7 in the axial direction X.
- the stator housing 17 is located between the low-pressure stage bearing housing 16A and the high-pressure stage bearing housing 16B in the axial direction X, and is adjacent to each of the low-pressure stage bearing housing 16A and the high-pressure stage bearing housing 16B.
- the low-pressure stage bearing housing 16A is arranged on the high-pressure stage side XH of the low-pressure stage housing 6 and on the low-pressure stage side XL of the stator housing 17.
- the low-pressure stage bearing housing 16A is mechanically connected to the low-pressure stage housing 6 and the stator housing 17, which are arranged adjacent to the low-pressure stage bearing housing 16A in the axial direction X, by fastening members such as fastening bolts.
- the high-pressure stage bearing housing 16B is arranged on the low-pressure stage side XL of the high-pressure stage housing 7 and on the high-pressure stage side XH of the stator housing 17 .
- the high-pressure stage bearing housing 16B is mechanically connected to the high-pressure stage housing 7 and the stator housing 17, which are arranged adjacent to the high-pressure stage bearing housing 16B in the axial direction X, by fastening members such as fastening bolts.
- fastening members such as fastening bolts.
- the electric centrifugal compressor 1 includes, between the low-pressure stage impeller 4 and the low-pressure stage-side bearing 15A in the axial direction X, a low-pressure stage-side sleeve 18A attached to the outer periphery of the rotary shaft 3, Between the high-pressure stage impeller 5 and the high-pressure stage-side bearing 15B in the direction X, a high-pressure stage-side sleeve 18B attached to the outer periphery of the rotating shaft 3 and pressurization that urges the high-pressure stage-side bearing 15B toward the low-pressure stage side XL a spring 19;
- the rotating body 11 described above further includes a low-pressure stage side sleeve 18A and a high-pressure stage side sleeve 18B.
- the low-pressure stage side bearing housing 16A has an inner surface (sleeve facing surface) 36 facing the outer peripheral surface 34 of the low-pressure stage side sleeve 18A and an end portion of the bearing support surface 161 on the low-pressure stage side XL extending radially inward. and a locking surface 164 on which the low-pressure stage side bearing 15A is locked.
- the inner surface 36 is formed to have a smaller diameter than the bearing support surface 161 .
- the high-pressure-stage bearing housing 16B has an inner surface (sleeve-facing surface) 165 facing the outer peripheral surface 181 of the high-pressure-stage-side sleeve 18B, and an end portion of the bearing support surface 162 on the high-pressure-stage side XH extending radially inward. and a retaining surface 166 .
- the inner surface 165 is formed to have a smaller diameter than the bearing support surface 162 .
- the above-described pressurizing spring 19 is arranged between the locking surface 166 and the high-pressure stage bearing 15B, and applies a predetermined pressurization to the high-pressure stage bearing 15B.
- FIG. 2 is a diagram showing a cross section of the electric centrifugal compressor 1 shown in FIG. 1 at a position different in the circumferential direction from the cross section shown in FIG.
- the cross section shown in FIG. 2 is also a cross section along the rotation axis CA.
- FIG. 3 is an enlarged view of the vicinity of the high pressure side sleeve 18B in the cross section shown in FIG.
- FIG. 4 is a diagram schematically showing the AA cross section of FIG.
- FIG. 5 is an enlarged view of the vicinity of the low-pressure stage sleeve 18A in the cross section shown in FIG.
- the high-pressure stage bearing housing 16B has a gap 25 (in the illustrated example, the outer peripheral surface 181 of the high-pressure stage sleeve 18B) between the rotor 11 including the rotating shaft 3 and the high pressure stage bearing housing 16B. and the inner surface 165 of the high pressure stage side bearing housing 16B).
- the compressed air supply hole 90 is formed as a through hole radially passing through the high pressure stage bearing housing 16B from the outer surface 168 to the inner surface 165 of the high pressure stage bearing housing 16B.
- An inlet 90a of the compressed air supply hole 90 is formed on the outer surface 168 of the high pressure stage bearing housing 16B, and an outlet 90b of the compressed air supply hole 90 is formed on the inner surface 165 of the high pressure stage bearing housing 16B.
- An outlet 90b of the compressed air supply hole 90 is positioned axially between the high pressure stage impeller 5 and the high pressure stage side bearing 15B.
- the electric centrifugal compressor 1 described above is configured to introduce compressed air from a pressure source (for example, the compressed air supply line 21 or the surge tank 27) into the inlet 90a of the compressed air supply hole 90.
- a pressure source for example, the compressed air supply line 21 or the surge tank 27
- a compressed air introduction line 26 is provided.
- the compressed air introduction line 26 is configured to introduce compressed air from each of the compressed air supply line 21 and the surge tank 27 into the inlet 90 a of the compressed air supply hole 90 .
- the gas in the surge tank 27 has a higher pressure than the space 24 described later by the compressor 28 .
- the compressed air introduction line 26 has a first pipe 261 connected on one side to the branch portion 211 of the compressed air supply line 21 and connected to the inlet 90a on the other side, and a first pipe 261 connected on one side to the surge tank on the other side. 27, and a switching device 263 configured to switch the supply source of compressed air to the inlet 90a to either the compressed air supply line 21 or the surge tank 27.
- a cooling device 265 for cooling the compressed air is provided on the compressed air supply line 21 . In another embodiment, the cooling device 265 may be provided upstream of the switching device 263 in the first pipe 261 (between the branch portion 211 and the switching device 263 in the first pipe 261).
- the switching device 263 may be a three-way valve provided at the connecting portion between the first pipe 261 and the second pipe 262 as shown in FIG. It may be a valve (for example, an on-off valve) provided on the upstream side of the section and on the second pipe 262 .
- the compressed air introduction line 26 includes a pipe having one side connected to the surge tank 27 and the other side connected to the inlet 90a, and the compressed air is supplied from only the surge tank 27 to the inlet 90a. may be configured to install By configuring so that compressed air can be supplied from the compressed air supply line 21 to the inlet 90a, the capacity of the surge tank 27 can be made small.
- a space 24 is formed between the back surface 57 of the high-pressure stage impeller 5 and the high-pressure stage side surface 167 of the high-pressure stage bearing housing 16B facing the back surface 57 .
- the outer peripheral surface 181 of the high-pressure stage sleeve 18B has an annular groove 182 in which a seal member (for example, an annular seal ring) 86 is fitted, and a seal member (for example, an annular groove 183 into which an annular seal ring 87 is fitted, and an annular groove 184 into which a seal member (eg, an annular seal ring) 88 is fitted are formed.
- a seal member for example, an annular seal ring
- the annular groove 182 is located between the high-pressure stage impeller 5 and the outlet 90b of the compressed air supply hole 90 in the axial direction X.
- the seal member 86 is provided so as to seal the gap 25 at a position between the high-pressure stage impeller 5 and the outlet 90 b of the compressed air supply hole 90 in the axial direction X. As shown in FIG.
- the annular groove 183 is located axially between the outlet 90b of the compressed air supply hole 90 and the high pressure stage side bearing 15B. Therefore, the outlet 90b of the compressed air supply hole 90 is positioned between the annular groove 182 and the annular groove 183 in the axial direction X. As shown in FIG.
- the seal member 87 is provided so as to seal the gap 25 between the outlet 90b of the compressed air supply hole 90 and the high pressure stage side bearing 15B in the axial direction.
- the annular groove 184 is located axially between the outlet 90b of the compressed air supply hole 90 and the high-pressure stage bearing 15B (more specifically, axially between the annular groove 183 and the high-pressure stage bearing 15B). .
- the seal member 88 has a gap at a position between the outlet of the compressed air supply hole 90 and the high pressure stage side bearing 15B in the axial direction (more specifically, between the annular groove 183 and the high pressure stage side bearing 15B in the axial direction). 25 is provided to seal.
- the outer surface of each of the sealing member 86, the sealing member 87, and the sealing member 88 is in contact with the outer peripheral surface 181 of the high pressure stage sleeve 18B, dividing the gap 25 into a plurality of parts.
- the high-pressure stage bearing housing 16B supplies compressed gas from the outside of the high-pressure stage bearing housing 16B to the gap 25 between the rotating body 11 including the rotating shaft 3 and the high-pressure stage bearing housing 16B.
- the outlet 90b of the compressed air supply hole 90 is formed in the inner surface 165 of the high pressure stage side bearing housing 16B, and the high pressure stage impeller 5 and the high pressure stage side bearing 15B in the axial direction X located between
- the compressed gas is supplied from the compressed air supply hole 90 to the gap 25, so that leakage flow from the space 24 facing the back surface 57 of the high pressure stage impeller 5 to the high pressure stage side bearing 15B can be suppressed.
- Compressed air is supplied from the compressed air introduction line 26 so that the pressure in the space 89 between the seal member 86 and the seal member 87 in the gap 25 is higher than the pressure in the space 24 adjacent to the back surface of the high-pressure stage impeller 5 .
- By supplying compressed air to the inlet 90a of the hole 90 it is possible to effectively suppress leakage flow from the space 24 facing the back surface 57 of the high-pressure stage impeller 5 to the high-pressure stage side bearing 15B.
- the pressure in the space 89 between the seal member 86 and the seal member 87 in the gap 25 increases the pressure in the space 79 (between the seal member 88 and the high pressure stage bearing 15B) that accommodates the high pressure stage side bearing 15B.
- the grease enclosed in the high-pressure stage side bearing 15B is released from the gap 25 and Leakage through the space 24 into the flow path in the high-pressure stage housing 7 can be suppressed.
- the mixture of grease in the compressed gas compressed by the electric centrifugal compressor 1 can be suppressed, so that the electric centrifugal compressor 1 can supply clean compressed gas to a fuel cell or the like.
- the high-pressure-stage bearing housing 16B has a purge valve for discharging the compressed air supplied from the compressed-air supply hole 90 to the gap 25 to the outside of the high-pressure-stage bearing housing 16B through the gap 25.
- the purge hole 92 is formed as a through hole that radially penetrates the high pressure stage bearing housing 16B from the outer surface 168 to the inner surface 165 of the high pressure stage bearing housing 16B.
- An inlet 92a of the purge hole 92 is formed in the inner surface 165 of the high-pressure stage bearing housing 16B and positioned between the high-pressure stage impeller 5 in the axial direction X and the high-pressure stage bearing 15B.
- an inlet 92a of the purge hole 92 is formed on the bearing support surface 162 on the side of the high-pressure stage impeller 5 and opens toward a space 99 in which the pressurizing spring 19 is accommodated.
- An outlet 92b of the purge hole 92 is formed on the outer surface 168 of the high pressure stage bearing housing 16B.
- the compressed air supplied to the clearance 25 is discharged to the outside of the high pressure stage bearing housing 16B through the purge hole 92, so that the compressed air supplied to the clearance 25 is discharged from the high pressure stage bearing 15B. can be suppressed from entering the interior of the As a result, the grease of the high-pressure stage bearing 15B can be prevented from becoming oil mist, and the durability and life of the high-pressure stage bearing 15B can be improved.
- the high-pressure stage side bearing 15B includes an inner ring 94, an outer ring 95, a plurality of balls 96 (a plurality of rolling elements) held between the inner ring 94 and the outer ring 95, and a shaft. and a pair of annular seal plates 97 positioned on each side of the ball 96 in the direction X and held by the outer ring 95 .
- an annular gap formed between the pair of annular seal plates 97 on the high-pressure stage impeller 5 side and the inner ring 94 is defined as a seal plate gap 98
- the axial direction of the seal plate gap 98 is defined as Assuming that the cross-sectional area orthogonal to X (the area of the annular seal plate gap 98 shown in FIG. 4) is S1, the purge hole 92 has a passage cross-sectional area S2 larger than the cross-sectional area S1.
- the purge hole 92 may have a passage cross-sectional area S2 that is larger than the cross-sectional area S1 from the inlet 92a to the outlet 92b.
- the passage cross-sectional area of the purge hole 92 means the cross-sectional area perpendicular to the flow direction of the compressed air in the purge hole 92 (the cross-sectional area perpendicular to the extending direction of the purge hole 92).
- the purge hole 92 has the passage cross-sectional area S2 larger than the cross-sectional area S1 of the seal plate gap 98, the compressed air supplied to the gap 25 is promoted to flow into the purge hole 92, thereby Compressed air can be suppressed from entering the inside of the high pressure stage bearing 15B. As a result, the grease of the high-pressure stage bearing 15B can be prevented from becoming oil mist, and the durability and life of the high-pressure stage bearing 15B can be improved.
- the low-pressure stage bearing housing 16A has a gap 38 between the rotating body 11 including the rotating shaft 3 and the low-pressure stage bearing housing 16A (in the illustrated example, the outer peripheral surface 34 of the low-pressure stage sleeve 18A). and the inner surface 36 of the low pressure stage side bearing housing 16A).
- the compressed air supply hole 91 is formed as a through hole radially passing through the high pressure stage bearing housing 16B from the outer surface 170 to the inner surface 36 of the low pressure stage bearing housing 16A.
- An inlet 91a of the compressed air supply hole 91 is formed on the outer surface 170 of the low pressure stage bearing housing 16A, and an outlet 91b of the compressed air supply hole 91 is formed on the inner surface 36 of the low pressure stage bearing housing 16A.
- An outlet 91b of the compressed air supply hole 91 is positioned axially between the low-pressure stage impeller 4 and the low-pressure stage side bearing 15A.
- the electric centrifugal compressor 1 described above includes a compressed air introduction line 29 configured to introduce compressed air from a pressure source (for example, the compressed air supply line 21 or the surge tank 27) into the inlet 91a of the compressed air supply hole 91.
- a pressure source for example, the compressed air supply line 21 or the surge tank 27
- the compressed air introduction line 29 shares some facilities (pipes and valves) with the compressed air introduction line 26 described above. That is, the compressed air introduction line 29 has one side connected to a branch portion 264 of the first pipe 261 located between the connection portion with the second pipe 262 and the inlet 91a, and the other side connected to the inlet 91a. 3 pipe 291 and a pressure reducing throttle valve 292 provided on the third pipe 291 . Note that in some other embodiments, the compressed air introduction line 29 may not share equipment with the compressed air introduction line 26 .
- a space 33 is formed between the back surface 30 of the low-pressure stage impeller 4 and the low-pressure stage side surface 32 of the low-pressure stage bearing housing 16A facing the back surface 30 .
- the outer peripheral surface 34 of the low-pressure stage sleeve 18A has an annular groove 203 in which a seal member (for example, an annular seal ring) 202 is fitted, and a seal member ( For example, an annular groove 205 into which an annular seal ring 204 is fitted is formed.
- a seal member for example, an annular seal ring
- the annular groove 203 is located between the low-pressure stage impeller 4 and the outlet 91b of the compressed air supply hole 91 in the axial direction X.
- the sealing member 202 is provided so as to seal the gap 38 at a position between the low-pressure stage impeller 4 and the outlet 91 b of the compressed air supply hole 91 in the axial direction X. As shown in FIG.
- the annular groove 205 is located axially between the outlet 91b of the compressed air supply hole 91 and the low pressure stage side bearing 15A. Therefore, the outlet 91b of the compressed air supply hole 91 is located between the annular groove 203 and the annular groove 205 in the axial direction X. As shown in FIG.
- the seal member 204 is provided so as to seal the gap 38 at a position between the outlet 91b of the compressed air supply hole 91 and the low pressure stage side bearing 15A in the axial direction.
- each of the sealing member 202 and the sealing member 204 is in contact with the outer peripheral surface 34 of the low-pressure stage sleeve 18A, dividing the gap 38 into a plurality of parts.
- the low-pressure stage impeller 4 rotates, the temperature and pressure of the gas existing in the space 33 rise. If the gas present in the space 33 flows through the gap 38 to the low-pressure stage bearing 15A, the grease of the low-pressure stage bearing 15A becomes oil mist, which may deteriorate the low-pressure stage bearing 15A.
- the low-pressure stage bearing housing 16A supplies compressed gas from the outside of the low-pressure stage bearing housing 16A to the gap 38 between the rotating body 11 including the rotating shaft 3 and the low-pressure stage bearing housing 16A.
- the outlet 91b of the compressed air supply hole 91 is formed in the inner surface 36 of the low pressure stage bearing housing 16A, and the low pressure stage impeller 4 and the low pressure stage bearing 15A in the axial direction X located between
- Compressed air is supplied from the compressed air introduction line 29 so that the pressure in the space 206 between the seal member 202 and the seal member 204 in the gap 38 is higher than the pressure in the space 33 adjacent to the back surface 30 of the low-pressure stage impeller 4 .
- By supplying compressed air to the inlet 91a of the supply hole 91 leakage flow from the space 33 adjacent to the back surface 30 of the low-pressure stage impeller 4 to the low-pressure stage bearing 15A can be effectively suppressed.
- the pressure in the space 206 between the seal member 202 and the seal member 204 in the gap 38 increases the pressure in the space 208 (between the seal member 204 and the low pressure stage side bearing 15A) that accommodates the low-pressure stage side bearing 15A in the gap 38.
- the grease enclosed in the low-pressure stage side bearing 15A is released from the gap 38 and Leakage through the space 33 into the flow path in the low-pressure stage housing 6 can be suppressed.
- the mixture of grease in the compressed gas compressed by the electric centrifugal compressor 1 can be suppressed, so that the electric centrifugal compressor 1 can supply clean compressed gas to a fuel cell or the like.
- the low-pressure stage bearing housing 16A has a purge valve for discharging the compressed air supplied from the compressed air supply hole 91 to the clearance 38 to the outside of the low-pressure stage bearing housing 16A through the clearance 38.
- FIGS. Includes holes 93 .
- the purge hole 93 is formed as a through hole radially passing through the low-pressure stage bearing housing 16A from the outer surface 170 to the inner surface 36 of the low-pressure stage bearing housing 16A.
- An inlet 93a of the purge hole 93 is formed in the inner surface 36 of the low-pressure stage bearing housing 16A and is located between the low-pressure stage impeller 4 and the low-pressure stage bearing 15A in the axial direction X (in the illustrated example, between the seal member 204 in the axial direction X). low-pressure stage side bearing 15A).
- An outlet 93b of the purge hole 93 is formed on the outer surface 170 of the low pressure stage bearing housing 16A.
- the compressed air supplied to the clearance 38 is discharged to the outside of the low-pressure stage bearing housing 16A through the purge hole 93, so that the compressed air supplied to the clearance 38 is discharged to the low-pressure stage bearing 15A.
- the grease of the low-pressure stage side bearing 15A can be prevented from becoming oil mist, and the durability and life of the low-pressure stage side bearing 15A can be improved.
- the low-pressure stage side bearing 15A includes an inner ring 212, an outer ring 213, a plurality of balls 214 as a plurality of rolling elements held between the inner ring 212 and the outer ring 213, and and a pair of annular seal plates 215 positioned on opposite sides of the ball 214 and held by the outer ring 213 .
- an annular gap formed between the pair of annular seal plates 215 on the high-pressure stage impeller 5 side and the inner ring 212 is defined as a seal plate gap 216, and the axial direction of the seal plate gap 216 is defined as Assuming that the cross-sectional area orthogonal to X is S3, the purge hole 93 has a passage cross-sectional area S4 that is larger than the cross-sectional area S1.
- the purge hole 93 may have a passage cross-sectional area S4 that is larger than the cross-sectional area S3 from the inlet 93a to the outlet 93b.
- the passage cross-sectional area of the purge hole 93 means the cross-sectional area perpendicular to the flow direction of the compressed air in the purge hole 93 (the cross-sectional area perpendicular to the extending direction of the purge hole 93).
- the purge hole 93 has a passage cross-sectional area larger than the cross-sectional area of the seal plate gap 216, the flow of the compressed air supplied to the gap 38 to the purge hole 93 is promoted, and the low pressure stage is discharged from the gap 38. Intrusion of compressed air into the side bearing 15A can be suppressed. As a result, the grease of the low-pressure stage side bearing 15A can be prevented from becoming oil mist, and the durability and life of the low-pressure stage side bearing 15A can be improved.
- FIG. 6 is an enlarged view of the vicinity of the high pressure stage side sleeve 18B of the electric centrifugal compressor 1 according to one embodiment, and schematically shows a cross section of the electric centrifugal compressor 1 along the rotation axis CA.
- the same reference numerals as in the configuration described above indicate the same configuration as the configuration described above, and the description thereof is omitted.
- three seal members 86 to 88 are provided on the outer peripheral surface 181 of the high pressure stage side sleeve 18B, but in some embodiments, for example, as shown in FIG. Only two sealing members 86 and 87 may be provided on the outer peripheral surface 181 of the stage-side sleeve 18B.
- the annular groove 182 is located between the high-pressure stage impeller 5 and the outlet 90b of the compressed air supply hole 90 in the axial direction X.
- the seal member 86 is provided so as to seal the gap 25 at a position between the high-pressure stage impeller 5 and the outlet 90 b of the compressed air supply hole 90 in the axial direction X. As shown in FIG.
- the annular groove 183 is located axially between the outlet 90b of the compressed air supply hole 90 and the high pressure stage side bearing 15B. Therefore, the outlet 90b of the compressed air supply hole 90 is positioned between the annular groove 182 and the annular groove 183 in the axial direction X. As shown in FIG.
- the seal member 87 is provided so as to seal the gap 25 between the outlet 90b of the compressed air supply hole 90 and the high pressure stage side bearing 15B in the axial direction.
- each of the sealing member 86 and the sealing member 87 is in contact with the outer peripheral surface 181 of the high-pressure stage sleeve 18B, dividing the gap 25 into a plurality of parts.
- the electric centrifugal compressor 1 has a rotating body 11 including the rotating shaft 3 and a high pressure stage bearing housing 16B at a position in the axial direction X between the seal member 87 and the high pressure stage bearing 15B.
- a lip seal 100 is provided to seal the gap 25 between (in the illustrated example, the gap between the outer peripheral surface 181 of the high pressure stage side sleeve 18B and the inner surface 165 of the high pressure stage side bearing housing 16B).
- the base end portion 100a of the lip seal 100 is fixed to the inner surface 165 of the high pressure stage bearing housing 16B, and the tip end portion 100b of the lip seal 100 is configured to contact the outer peripheral surface 181 of the rotating body 11. As shown in FIG.
- the inner surface 165 of the high pressure stage side bearing housing 16B includes a first inner surface 165a in which the outlet 90b of the compressed air supply hole 90 is formed, and a first inner surface 165a connected to the first inner surface 165a via a stepped surface 165b. 2 inner surface 165c.
- the second inner surface 165c has a larger diameter than the first inner surface 165a and a smaller diameter than the bearing support surface.
- the lip seal 100 has a base end portion 100a fixed to the second inner surface 165c, and extends radially inward along the stepped surface 165b from the end portion of the base end portion 100a on the high pressure stage impeller 5 side in the axial direction X.
- first connecting portion 100c a first connecting portion 100c
- second connecting portion 100d connecting the inner peripheral end of the first connecting portion 100c and the tip portion 100b
- tip portion 100b intersects with the axial direction X and the radial direction Y so as to move toward the high pressure stage side bearing 15B side in the axial direction as it goes radially inward from the inner peripheral end of the first connection portion 100c. It extends obliquely.
- the tip portion 100b of the lip seal 100 is formed thicker than each of the base end portion 100a, the first connection portion 100c, and the second connection portion 100d.
- the outer peripheral surface 181 of the high-pressure-stage sleeve 18B includes a large-diameter portion 181a and a small-diameter portion 181b having a smaller diameter than the large-diameter portion 181a.
- the large-diameter portion 181a is located between the small-diameter portion 181b and the high-pressure stage impeller 5 and is adjacent to the small-diameter portion 181b and the high-pressure stage impeller 5 respectively.
- the annular grooves 182 and 183 are formed in the large diameter portion 181a, and the tip portion 100b of the lip seal 100 is configured to be able to contact the small diameter portion 181b.
- the compressed air supplied from the compressed air supply hole 90 to the gap 25 is The air pressure does not separate the tip portion 100b of the lip seal 100 from the outer peripheral surface 181 of the high pressure side sleeve 18B. Therefore, as shown in FIG. 6, the compressed air supplied to the gap 25 flows into the space 24 between the back surface 57 of the high-pressure stage impeller 5 and the high-pressure stage side surface 167, and almost reaches the high-pressure stage bearing 15B side. Not flowing.
- the pressure of the compressed air supplied from the compressed air supply hole 90 to the gap 25 pushes the tip portion 100b of the lip seal 100 to the outer peripheral surface of the high pressure side sleeve 18B. away from 181; Therefore, as shown in FIG. 7, the compressed air supplied to the gap 25 flows into the space 24 between the back surface 57 of the high-pressure stage impeller 5 and the high-pressure stage side surface 167, and also flows toward the high-pressure stage side bearing 15B. and discharged from the purge hole 92 .
- the tip portion 100b of the lip seal 100 is separated from the outer peripheral surface 181 of the high-pressure stage sleeve 18B. It is possible to effectively suppress an increase in the load on the electric motor 10 due to contact between the tip portion 100b of the sleeve 18B and the outer peripheral surface 181 of the high-pressure stage side sleeve 18B.
- the electric centrifugal compressor 1 includes a magnetic body 219 (for example, iron) fixed to the tip portion 100b of the lip seal 100 and the tip portion 100b of the lip seal 100.
- An electromagnet 220 for separating from the outer peripheral surface 181 of the rotating body 11, a power supply unit 222 configured to apply a current to the electromagnet 220, a rotation speed sensor 224 for measuring the rotation speed of the rotating shaft 3, and a power supply unit. 222 is provided.
- the magnetic body 219 is fixed to the surface of the tip portion 100b of the lip seal 100 opposite to the high-pressure stage sleeve 18B.
- the power control unit 226 may be composed of an electric circuit or may be composed of a computer.
- a storage device such as RAM (Random Access Memory) and ROM (Read Only Memory)
- a processor such as CPU (Central Processing Unit) and GPU (Graphics Processing Unit) and the processor implements its functions by executing the program stored in the storage device.
- the power control unit 226 is configured to apply current to the electromagnet 220 based on the rotation speed of the rotating shaft 3 measured by the rotation speed sensor 224 . For example, when the rotation speed of the rotating shaft 3 measured by the rotation speed sensor 224 exceeds a reference value, the power control unit 226 applies current to the electromagnet 220 to move the tip portion 100 b of the lip seal 100 to the outer circumference of the rotating body 11 . It may be configured to be spaced from surface 181 .
- the power control unit 226 when the rotation speed of the rotating shaft 3 measured by the rotation speed sensor 224 is equal to or lower than the reference value, the power control unit 226 does not energize the electromagnet 220.
- the tip portion 100b of the lip seal 100 is not separated from the outer peripheral surface 181 of the high-pressure-stage sleeve 18B only by the pressure of the compressed air supplied to the gap 25 from. Therefore, as shown in FIG. 8, the compressed air supplied to the gap 25 flows into the space 24 between the back surface 57 of the high-pressure stage impeller 5 and the high-pressure stage side surface 167, and almost reaches the high-pressure stage bearing 15B side. Not flowing.
- the power supply control unit 226 controls the power supply unit 222 to apply current to the electromagnet 220, thereby 219 and the tip portion 100b to which the magnetic body 219 is fixed can be attracted to the electromagnet 220 to separate the tip portion 100b from the outer peripheral surface 181 of the high pressure stage sleeve 18B.
- the compressed air supplied to the gap 25 flows into the space 24 between the back surface 57 of the high-pressure stage impeller 5 and the high-pressure stage side surface 167, and also flows toward the high-pressure stage side bearing 15B. and discharged from the purge hole 92 .
- the tip portion 100b of the lip seal 100 is separated from the outer peripheral surface 181 of the high pressure side sleeve 18B more reliably than the configurations shown in FIGS. It is possible to effectively suppress an increase in the load on the electric motor 10 due to contact between the tip portion 100b of the lip seal 100 and the outer peripheral surface 181 of the high-pressure stage sleeve 18B when the rotation speed of the rotating shaft 3 is high.
- the electric centrifugal compressor 1 may further include a negative pressure pump 230 for sucking air from each of the purge holes 92 and 93, as shown in FIG. 10, for example.
- the electric centrifugal compressor 1 shown in FIG. Further prepare.
- the electric centrifugal compressor 1 shown in FIG. 10 further includes a pump control section 236 that controls the negative pressure pump 230.
- the pump control section 236 operates the negative pressure pump 230 when the electric motor 10 is stopped so as to open the purge hole. Air is sucked out from each of the purge holes 92 and 93 .
- the pump control unit 236 may be composed of an electric circuit or may be composed of a computer.
- the pump control unit 236 includes a storage device such as RAM (Random Access Memory) and ROM, and a processor such as CPU and GPU, and the processor executes programs stored in the storage device. By executing it, the function is realized.
- the negative pressure pump 230 is operated to evacuate the internal air of the high-pressure stage bearing housing 16B from the purge hole 92, whereby the pressure inside the high-pressure stage bearing 15B is reduced. It is possible to prevent the enclosed grease from leaking into the flow path in the high-pressure stage housing 7 through the clearance 25 and the space 24 .
- the negative pressure pump 230 is operated to evacuate the internal air of the low-pressure stage bearing housing 16A from the purge hole 93, thereby removing the grease sealed in the low-pressure stage bearing 15A from the gap. Leakage into the flow path in the low-pressure stage housing 6 through 38 and space 33 can be suppressed.
- a multi-stage electric centrifugal compressor was exemplified, but in other embodiments, a single-stage electric centrifugal compressor may be used.
- the electric centrifugal compressor 1 rotates the rotating shaft 3 at a position between the seal member 87 and the high pressure stage side bearing 15B in the axial direction X.
- a lip seal 100 is provided to seal a gap 25 between the rotating body 11 and the high-pressure stage side bearing housing 16B.
- the electric centrifugal compressor 1, for example in the configuration shown in FIG. A lip seal may be provided to seal the gap 38 with the low pressure stage bearing housing 16A.
- the electric centrifugal compressor (for example, the electric centrifugal compressor 1 described above) according to the present disclosure is an electric motor (eg, the electric motor 10 described above) including a rotating shaft (eg, the rotating shaft 3 described above); a first impeller (for example, the low-pressure stage impeller 4 or the high-pressure stage impeller 5 described above) provided on one end side of the rotating shaft; A first bearing (e.g., the low pressure side bearing 15A or the high pressure side bearing 15A described above) rotatably supports the rotating shaft at a position between the first impeller and the electric motor and contains a lubricant (e.g., the grease described above).
- a lubricant e.g., the grease described above
- first bearing housing that accommodates the first bearing (for example, the low-pressure stage bearing housing 16A or the high-pressure stage bearing housing 16B described above); with The first bearing housing is arranged such that a rotating body (for example, the above-described rotating body 11) including the rotating shaft and a gap (for example, the above-described gap 25 or 38) between the first bearing housing and the outside of the first bearing housing.
- a rotating body for example, the above-described rotating body 11
- a gap for example, the above-described gap 25 or 38
- a compressed gas supply hole for supplying compressed gas for example, the compressed air supply hole 90 or the compressed air supply hole 91 described above
- the outlet of the compressed gas supply hole is provided on the inner surface of the first bearing housing and is between the first impeller and the first bearing in the axial direction of the rotating shaft. To position.
- the compressed gas is supplied from the compressed gas supply hole of the first bearing housing to the gap between the rotor and the first bearing housing, the back surface of the first impeller Leakage flow from the adjacent space to the first bearing can be suppressed.
- it is possible to suppress deterioration of the lubricant in the first bearing caused by the leakage flow, thereby realizing improvement in durability and extension of the life of the first bearing.
- a first seal member for example, seal member 86 or seal member 202 described above
- a second seal member e.g., seal member 87, seal member 88 or seal 88 described above
- seal member 204 Further prepare.
- the outlet of the compressed gas supply hole is provided in the space between the first seal member and the second seal member in the gap between the rotor and the first bearing housing.
- a third seal member for example, the above-described seal member 88 provided to seal the gap between the second seal member (for example, the above-described seal member 87) and the first bearing in the axial direction. Further prepare.
- the lubricant of the first bearing flows through the first impeller through the gap between the rotating body and the first bearing housing and the space adjacent to the back surface of the first impeller. Leakage to the mainstream side can be effectively suppressed.
- a compressed gas introduction line (for example, the above-mentioned compressed air introduction line 26 or compressed air introduction line 29) configured to introduce the compressed gas into the inlet of the compressed gas supply hole (for example, the above-mentioned inlet 90a or 91a) Further prepare.
- the pressure in the space between the first seal member and the second seal member in the gap is made higher than the pressure in the space adjacent to the rear surface of the first impeller.
- a lip seal (eg, the lip seal 100 described above) is provided to seal the gap at a position between the second seal member and the first bearing in the axial direction.
- the base end portion of the lip seal (for example, the above-mentioned base end portion 100a) is fixed to the first bearing housing, and the tip portion of the lip seal (for example, the above-mentioned tip portion 100b) is in contact with the outer peripheral surface of the rotating body. configured as possible.
- It further comprises an electromagnet (for example, electromagnet 220 described above) for separating the tip of the lip seal from the outer peripheral surface of the rotating body.
- an electromagnet for example, electromagnet 220 described above
- a power supply unit (e.g., power supply unit 222 described above) configured to apply current to the electromagnet;
- a rotation speed sensor for example, the rotation speed sensor 224 described above
- a power control unit for example, the power control unit 226 described above
- the power control unit is configured to apply current to the electromagnet based on the rotation speed of the rotating shaft measured by the rotation speed sensor.
- the power supply control unit applies current to the electromagnet to move the tip of the lip seal from the outer peripheral surface of the rotating body. configured to be spaced apart.
- the load on the electric motor increases due to contact between the tip of the lip seal and the outer peripheral surface of the rotating body when the rotation speed of the rotating shaft is greater than the reference value. can be effectively suppressed.
- the first bearing housing has a purge hole (for example, the purge hole 92 or the purge hole described above) for discharging the compressed gas supplied to the gap from the compressed gas supply hole to the outside of the first bearing housing through the gap.
- a purge hole for example, the purge hole 92 or the purge hole described above
- the inlet of the purge hole is provided on the inner surface of the first bearing housing and is located between the first impeller and the first bearing in the axial direction.
- the compressed gas supplied to the gap between the rotor and the first bearing housing is discharged to the outside of the first bearing housing through the purge hole.
- Compressed gas supplied to the gap can be suppressed from entering the inside of the first bearing.
- the deterioration of the lubricant in the first bearing can be suppressed, and the durability and life of the first bearing can be improved.
- the first bearing includes an inner ring (for example, the above-described inner ring 94 or inner ring 212), an outer ring (for example, the above-described outer ring 95 or outer ring 213), and a plurality of rolling elements (for example, the above-described rolling elements) held between the inner ring and the outer ring.
- an inner ring for example, the above-described inner ring 94 or inner ring 212
- an outer ring for example, the above-described outer ring 95 or outer ring 213
- a plurality of rolling elements for example, the above-described rolling elements
- annular seal plates for example, the above-described pair of annular seal plates 97 or a pair of an annular seal plate 215) of Of the pair of annular seal plates, an annular gap formed between the first impeller-side annular seal plate and the inner ring is defined as a seal plate gap (for example, the seal plate gap 98 or the seal plate gap 216 described above). Then, The passage cross-sectional area of the purge hole is larger than the cross-sectional area of the seal plate gap perpendicular to the axial direction.
- the purge hole has a passage cross-sectional area larger than the cross-sectional area of the seal plate gap
- the compression supplied to the gap between the rotating body and the first bearing housing is It is possible to prevent the compressed gas from entering the first bearing through the gap between the rotating body and the first bearing housing by promoting the flow of the gas to the purge hole.
- the deterioration of the lubricant in the first bearing can be suppressed, and the durability and life of the first bearing can be improved.
- a negative pressure pump (for example, the negative pressure pump 230 described above) is further provided for sucking gas from the purge hole.
- the negative pressure pump when the electric motor is stopped, the negative pressure pump is operated to suck out the internal air of the first bearing housing from the purge hole, thereby rotating the lubricant in the first bearing. It is possible to suppress leakage into the flow path of the main stream flowing through the first impeller through the gap between the body and the first shaft housing and the space adjacent to the back surface of the first impeller.
- the electric centrifugal compressor described in (12) above further comprising a pump control unit (for example, the pump control unit 236 described above) for controlling the negative pressure pump;
- the pump control section is configured to operate the negative pressure pump when the electric motor is stopped.
- the negative pressure pump when the electric motor is stopped, the negative pressure pump is automatically operated to suck out the internal air of the first bearing housing from the purge hole, thereby removing the lubricant from the first bearing. can be suppressed from leaking into the flow path of the main stream flowing through the first impeller through the gap between the rotating body and the first shaft housing and the space adjacent to the back surface of the first impeller.
- the electric centrifugal compressor is a multi-stage electric centrifugal compressor, a second impeller (for example, the above-described low-pressure stage impeller 4 or high-pressure stage impeller 5) provided on the other end side of the rotating shaft;
- a second bearing e.g., the low-pressure stage bearing 15A or the high-pressure stage bearing 15A described above
- a second bearing housing that accommodates the second bearing (for example, the low-pressure stage bearing housing 16A or the high-pressure stage bearing housing 16B described above); with
- the second bearing housing has a compressed gas supply hole (for example, the above-mentioned compression valve) for supplying compressed gas to the gap (for example, the above-mentioned gap 25 or the above-mentioned gap 38
- a low-pressure stage housing for example, the low-pressure stage housing 6 described above
- a high-pressure stage housing for example, the high-pressure stage housing 7 described above
- a connecting pipe for example, the connecting pipe 8 described above
- the high-pressure stage housing has a high-pressure stage inlet opening (for example, the high-pressure stage inlet opening 71 described above) that opens in a direction that intersects the axis of the rotating shaft,
- the tie pipe is connected to the high pressure stage inlet opening.
- the high-pressure stage housing has a high-pressure stage inlet opening in a direction that intersects with the axis of the rotating shaft, and the connecting pipe is connected to the high-pressure stage inlet opening. is connected. Therefore, the compressed gas compressed by the first impeller is supplied to the inside of the high pressure stage housing from the outer peripheral side of the high pressure stage housing through the connecting pipe. In this case, compared to the case where the compressed gas is introduced into the high pressure stage housing along the axial direction of the rotating shaft, the length of the connecting pipe and the high pressure stage housing in the axial direction can be shortened.
- the length of the multistage electric centrifugal compressor in the axial direction can be shortened, so that the size and weight of the multistage electric centrifugal compressor can be reduced.
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Abstract
Description
本願は、2021年2月12日に日本国特許庁に出願された特願2021-020356号に基づき優先権を主張し、その内容をここに援用する。
回転シャフトを含む電動モータと、
前記回転シャフトの一端側に設けられた第1インペラと、
前記第1インペラと前記電動モータとの間の位置で前記回転シャフトを回転可能に支持し、潤滑剤を含む第1軸受と、
前記第1軸受を収容する第1軸受ハウジングと、
を備え、
前記第1軸受ハウジングは、前記回転シャフトを含む回転体と前記第1軸受ハウジングとの隙間に前記第1軸受ハウジングの外部から圧縮気体を供給するための圧縮気体供給孔を含み、
前記圧縮気体供給孔の出口は、前記第1軸受ハウジングの内面に設けられ、前記回転シャフトの軸方向における前記第1インペラと前記第1軸受との間に位置する。
例えば、「ある方向に」、「ある方向に沿って」、「平行」、「直交」、「中心」、「同心」或いは「同軸」等の相対的或いは絶対的な配置を表す表現は、厳密にそのような配置を表すのみならず、公差、若しくは、同じ機能が得られる程度の角度や距離をもって相対的に変位している状態も表すものとする。
例えば、「同一」、「等しい」及び「均質」等の物事が等しい状態であることを表す表現は、厳密に等しい状態を表すのみならず、公差、若しくは、同じ機能が得られる程度の差が存在している状態も表すものとする。
例えば、四角形状や円筒形状等の形状を表す表現は、幾何学的に厳密な意味での四角形状や円筒形状等の形状を表すのみならず、同じ効果が得られる範囲で、凹凸部や面取り部等を含む形状も表すものとする。
一方、一の構成要素を「備える」、「含む」、又は、「有する」という表現は、他の構成要素の存在を除外する排他的な表現ではない。
なお、同様の構成については同じ符号を付し説明を省略することがある。
図1は、本開示の一実施形態にかかる電動遠心圧縮機1の構成を概略的に示す概略構成図である。図1において、電動遠心圧縮機1は、回転シャフト3の回転軸線CAに沿った断面が概略的に示されている。
本開示の幾つかの実施形態にかかる電動遠心圧縮機1は、図1に示されるように、回転シャフト3の両端に設けられたインペラ(低圧段インペラ4、高圧段インペラ5)を電動モータ10により駆動するように構成された多段電動遠心圧縮機である。
電動遠心圧縮機1に搭載される電動モータ10は、回転子である回転体11と、固定子であるモータステータ12と、モータステータ12を収容するように構成されたステータハウジング17とを含む。回転体11は、回転シャフト3と、回転シャフト3の外周に取り付けられたロータアッセンブリ13とを含む。ロータアッセンブリ13は、永久磁石14を含む。モータステータ12は、ロータアッセンブリ13の外周を囲むように配置されており、ステータハウジング17の内部においてステータハウジング17に支持されている。モータステータ12は、モータコイル(ステータコイル)121を含み、不図示の電力源から供給された電力により、永久磁石14を搭載した回転体11を回転させる磁界を発生させるように構成されている。モータステータ12が発生させた磁界(電動モータ10が発生させた動力)により回転体11が回転すると、回転シャフト3に取り付けられたインペラ(低圧段インペラ4および高圧段インペラ5)が連動して回転する。
低圧段ハウジング6は、図1に示されるように、低圧段ハウジング6の外部から内部に気体を導入するための低圧段入口開口61と、低圧段ハウジング6の内部から外部に気体を排出するための低圧段出口開口62と、が形成されている。低圧段ハウジング6の内部には、低圧段入口開口61から低圧段ハウジング6の内部に導入された気体を低圧段インペラ4に導くための供給流路63と、低圧段インペラ4を通過した気体を低圧段出口開口62に導くためのスクロール流路64と、が形成されている。図示される実施形態では、低圧段入口開口61は、軸方向Xにおける低圧段側XLに向かって開口している。低圧段出口開口62は、回転軸線CAに対して交差(例えば、直交)する方向に向かって開口している。
高圧段ハウジング7は、図1に示されるように、高圧段ハウジング7の外部から内部に気体を導入するための高圧段入口開口71と、高圧段ハウジング7の内部から外部に気体を排出するための高圧段出口開口72と、が形成されている。高圧段ハウジング7の内部には、高圧段入口開口71から高圧段ハウジング7の内部に導入された気体を高圧段インペラ5に導くための供給流路73と、高圧段インペラ5を通過した気体を高圧段出口開口72に導くためのスクロール流路74と、が形成されている。図示される実施形態では、高圧段入口開口71および高圧段出口開口72の夫々は、回転軸線CAに対して交差(例えば、直交)する方向に向かって開口している。
図1に示すように、電動遠心圧縮機1は、低圧段インペラ4により圧縮された圧縮気体を高圧段ハウジング7に供給するためのつなぎ配管8を備えている。つなぎ配管8は、図1に示されるように、その長さ方向に沿って延びる管状に形成されており、上述した高圧段入口開口71に接続される高圧段側接続部81と、低圧段出口開口62に接続される低圧段側接続部82と、を少なくとも含む。図示される実施形態では、高圧段側接続部81および低圧段側接続部82の夫々は、回転シャフト3の回転軸線CAに対して交差(図示例では直交)する方向に沿って延在している。
低圧段側軸受15Aは、低圧段インペラ4と電動モータ10との間(低圧段インペラ4とロータアッセンブリ13との間)の位置で回転シャフト3を回転可能に支持している。低圧段側軸受15Aは、予め潤滑剤としてのグリースを封入したグリース封入式のボール軸受からなる。なお、ボール軸受は、空気軸受と比較して、アイドリングが不要であり、複雑なシステムが不要であり、市場性が良く、回転シャフト3の回転と停止の繰り返しに対する耐久性に優れている。
高圧段側軸受15Bは、予め潤滑剤としてのグリースを封入したグリース封入式のボール軸受からなる。
低圧段側軸受ハウジング16Aは、低圧段側軸受15Aを収容しており、低圧段側軸受15Aは、低圧段側軸受ハウジング16Aの内部に形成された軸受支持面161に支持されている。高圧段側軸受ハウジング16Bは、高圧段側軸受15Bを収容しており、高圧段側軸受15Bは、高圧段側軸受ハウジング16Bの内部に形成された軸受支持面162に支持されている。
図示される実施形態では、電動遠心圧縮機1は、軸方向Xにおける低圧段インペラ4と低圧段側軸受15Aとの間において、回転シャフト3の外周に取り付けられた低圧段側スリーブ18Aと、軸方向Xにおける高圧段インペラ5と高圧段側軸受15Bとの間において、回転シャフト3の外周に取り付けられた高圧段側スリーブ18Bと、高圧段側軸受15Bを低圧段側XLに付勢する与圧バネ19と、をさらに備える。上述した回転体11は、低圧段側スリーブ18Aと、高圧段側スリーブ18Bと、をさらに含む。
図2又は図3に示すように、高圧段側軸受ハウジング16Bは、回転シャフト3を含む回転体11と高圧段側軸受ハウジング16Bとの隙間25(図示例では高圧段側スリーブ18Bの外周面181と高圧段側軸受ハウジング16Bの内面165との隙間)に圧縮空気を供給するための圧縮空気供給孔90を含む。圧縮空気供給孔90は、高圧段側軸受ハウジング16Bの外面168から内面165にかけて高圧段側軸受ハウジング16Bを径方向に沿って貫通する貫通孔として形成されている。圧縮空気供給孔90の入口90aは、高圧段側軸受ハウジング16Bの外面168に形成されており、圧縮空気供給孔90の出口90bは、高圧段側軸受ハウジング16Bの内面165に形成されている。圧縮空気供給孔90の出口90bは、軸方向における高圧段インペラ5と高圧段側軸受15Bとの間に位置する。
図2又は図3に示すように、高圧段側軸受ハウジング16Bは、圧縮空気供給孔90から隙間25に供給された圧縮空気を隙間25から高圧段側軸受ハウジング16Bの外部に排出するためのパージ孔92(パージ通路)を含む。パージ孔92は、高圧段側軸受ハウジング16Bの外面168から内面165にかけて高圧段側軸受ハウジング16Bを径方向に沿って貫通する貫通孔として形成されている。パージ孔92の入口92aは、高圧段側軸受ハウジング16Bの内面165に形成され、軸方向Xにおける高圧段インペラ5と高圧段側軸受15Bとの間に位置する。図3に示す例ではパージ孔92の入口92aは、軸受支持面162における高圧段インペラ5側に形成されており、与圧バネ19が収容される空間99に向けて開口している。パージ孔92の出口92bは、高圧段側軸受ハウジング16Bの外面168に形成されている。
図2又は図5に示すように、低圧段側軸受ハウジング16Aは、回転シャフト3を含む回転体11と低圧段側軸受ハウジング16Aとの隙間38(図示例では低圧段側スリーブ18Aの外周面34と低圧段側軸受ハウジング16Aの内面36との隙間)に圧縮空気を供給するための圧縮空気供給孔91を含む。圧縮空気供給孔91は、低圧段側軸受ハウジング16Aの外面170から内面36にかけて高圧段側軸受ハウジング16Bを径方向に沿って貫通する貫通孔として形成されている。圧縮空気供給孔91の入口91aは、低圧段側軸受ハウジング16Aの外面170に形成されており、圧縮空気供給孔91の出口91bは、低圧段側軸受ハウジング16Aの内面36に形成されている。圧縮空気供給孔91の出口91bは、軸方向における低圧段インペラ4と低圧段側軸受15Aとの間に位置する。
図2及び図5に示すように、低圧段側軸受ハウジング16Aは、圧縮空気供給孔91から隙間38に供給された圧縮空気を隙間38から低圧段側軸受ハウジング16Aの外部に排出するためのパージ孔93を含む。パージ孔93は、低圧段側軸受ハウジング16Aの外面170から内面36にかけて低圧段側軸受ハウジング16Aを径方向に沿って貫通する貫通孔として形成されている。パージ孔93の入口93aは、低圧段側軸受ハウジング16Aの内面36に形成され、軸方向Xにおける低圧段インペラ4と低圧段側軸受15Aとの間(図示例では軸方向Xにおけるシール部材204と低圧段側軸受15Aとの間)に位置する。パージ孔93の出口93bは、低圧段側軸受ハウジング16Aの外面170に形成されている。
図6は、一実施形態に係る電動遠心圧縮機1の高圧段側スリーブ18B近傍の拡大図であり、電動遠心圧縮機1の回転軸線CAに沿った断面を概略的に示している。以下で示す構成において、前述の構成と共通の符号は、特記しない限り前述の構成と同様の構成を示すものとし、説明を省略する。
幾つかの実施形態では、例えば図10に示すように、電動遠心圧縮機1は、パージ孔92及びパージ孔93の各々から空気を吸い出すための負圧ポンプ230を更に備えていてもよい。図10に示す電動遠心圧縮機1は、パージ孔92の出口92bと負圧ポンプ230とを接続するパージライン232と、パージ孔93の出口93bと負圧ポンプ230とを接続するパージライン234とを更に備える。
回転シャフト(例えば上述の回転シャフト3)を含む電動モータ(例えば上述の電動モータ10)と、
前記回転シャフトの一端側に設けられた第1インペラ(例えば上述の低圧段インペラ4又は高圧段インペラ5)と、
前記第1インペラと前記電動モータとの間の位置で前記回転シャフトを回転可能に支持し、潤滑剤(例えば上述のグリース)を含む第1軸受(例えば上述の低圧段側軸受15A又は高圧段側軸受15B)と、
前記第1軸受を収容する第1軸受ハウジング(例えば上述の低圧段側軸受ハウジング16A又は高圧段側軸受ハウジング16B)と、
を備え、
前記第1軸受ハウジングは、前記回転シャフトを含む回転体(例えば上述の回転体11)と前記第1軸受ハウジングとの隙間(例えば上述の隙間25又は隙間38)に前記第1軸受ハウジングの外部から圧縮気体を供給するための圧縮気体供給孔(例えば上述の圧縮空気供給孔90又は圧縮空気供給孔91)を含み、
前記圧縮気体供給孔の出口(例えば上述の出口90b又は出口91b)は、前記第1軸受ハウジングの内面に設けられ、前記回転シャフトの軸方向における前記第1インペラと前記第1軸受との間に位置する。
前記軸方向における前記第1インペラと前記圧縮気体供給孔の前記出口との間の位置において前記隙間をシールするように設けられた第1シール部材(例えば上述のシール部材86又はシール部材202)と、
前記軸方向における前記圧縮気体供給孔の前記出口と前記第1軸受との間の位置において前記隙間をシールするように設けられた第2シール部材(例えば上述のシール部材87、シール部材88又はシール部材204)と、
を更に備える。
前記軸方向における前記第2シール部材(例えば上述のシール部材87)と前記第1軸受との間の位置において前記隙間をシールするように設けられた第3シール部材(例えば上述のシール部材88)を更に備える。
前記隙間のうち前記第1シール部材と前記第2シール部材との間の空間の圧力が前記第1インペラの背面に隣接する空間(例えば上述の空間24又は空間33)の圧力よりも大きくなるように、前記圧縮気体供給孔の入口(例えば上述の入口90a又は91a)に前記圧縮気体を導入するように構成された圧縮気体導入ライン(例えば上述の圧縮空気導入ライン26又は圧縮空気導入ライン29)を更に備える。
前記軸方向における前記第2シール部材と前記第1軸受との間の位置において前記隙間をシールするように設けられたリップシール(例えば上述のリップシール100)を更に備える。
前記リップシールの基端部(例えば上述の基端部100a)は前記第1軸受ハウジングに固定され、前記リップシールの先端部(例えば上述の先端部100b)は前記回転体の外周面に当接可能に構成される。
前記リップシールの先端部を前記回転体の外周面から離間させるための電磁石(例えば上述の電磁石220)を更に備える。
前記電磁石に電流を印加するように構成された電源ユニット(例えば上述の電源ユニット222)と、
前記回転シャフトの回転数を計測するための回転数センサ(例えば上述の回転数センサ224)と、
前記電源ユニットを制御するための電源制御部(例えば上述の電源制御部226)と、
を備え、
前記電源制御部は、前記回転数センサによって計測した前記回転シャフトの回転数に基づいて、前記電磁石に電流を流すように構成される。
前記電源制御部は、前記回転数センサによって計測した前記回転シャフトの回転数が基準値を超えた場合に、前記電磁石に電流を流して前記リップシールの前記先端部を前記回転体の外周面から離間させるように構成される。
前記第1軸受ハウジングは、前記圧縮気体供給孔から前記隙間に供給された前記圧縮気体を前記隙間から前記第1軸受ハウジングの外部に排出するためのパージ孔(例えば上述のパージ孔92又はパージ孔93)を含み、
前記パージ孔の入口(例えば上述の入口92a又は入口93a)は、前記第1軸受ハウジングの内面に設けられ、前記軸方向における前記第1インペラと前記第1軸受との間に位置する。
前記第1軸受は、内輪(例えば上述の内輪94又は内輪212)と、外輪(例えば上述の外輪95又は外輪213)と、前記内輪と外輪との間に保持された複数の転動体(例えば上述の複数のボール96又は複数のボール214)と、前記軸方向において前記転動体の両側にそれぞれ位置し、前記外輪に保持された一対の環状シール板(例えば上述の一対の環状シール板97又は一対の環状シール板215)と、を含み、
前記一対の環状シール板のうち前記第1インペラ側の環状シール板と前記内輪との間に形成される環状の隙間をシール板隙間(例えば上述のシール板隙間98又はシール板隙間216)と定義すると、
前記パージ孔の通路断面積は、前記シール板隙間の前記軸方向に直交する断面積よりも大きい。
前記パージ孔から気体を吸い出すための負圧ポンプ(例えば上述の負圧ポンプ230)を更に備える。
前記負圧ポンプを制御するためのポンプ制御部(例えば上述のポンプ制御部236)を更に備え、
前記ポンプ制御部は、前記電動モータの停止時に前記負圧ポンプを作動させるように構成される。
前記電動遠心圧縮機は、多段電動遠心圧縮機であり、
前記回転シャフトの他端側に設けられた第2インペラ(例えば上述の低圧段インペラ4又は高圧段インペラ5)と、
前記第2インペラと前記電動モータとの間の位置で前記回転シャフトを回転可能に支持し、潤滑剤(例えば上述のグリース)を含む第2軸受(例えば上述の低圧段側軸受15A又は高圧段側軸受15B)と、
前記第2軸受を収容する第2軸受ハウジング(例えば上述の低圧段側軸受ハウジング16A又は高圧段側軸受ハウジング16B)と、
を備え、
前記第2軸受ハウジングは、前記回転シャフトを含む回転体と前記第2軸受ハウジングとの隙間(例えば上述の隙間25又は隙間38)に圧縮気体を供給するための圧縮気体供給孔(例えば上述の圧縮空気供給孔90又は圧縮空気供給孔91)を含み、
前記第2軸受ハウジングの前記圧縮気体供給孔の出口(例えば上述の出口90b又は出口91b)は、前記軸方向における前記第2インペラと前記第2軸受との間に位置する。
前記第1インペラを収納する低圧段ハウジング(例えば上述の低圧段ハウジング6)と、
前記第2インペラを収納する高圧段ハウジング(例えば上述の高圧段ハウジング7)と、
前記第1インペラにより圧縮された圧縮気体を前記高圧段ハウジングに供給するためのつなぎ配管(例えば上述のつなぎ配管8)と、を備え、
前記高圧段ハウジングは、前記回転シャフトの軸線に対して交差する方向に向かって開口する高圧段入口開口(例えば上述の高圧段入口開口71)を有し、
前記つなぎ配管は、前記高圧段入口開口に接続される。
3 回転シャフト
4 低圧段インペラ
5 高圧段インペラ
6 低圧段ハウジング
7 高圧段ハウジング
8 つなぎ配管
10 電動モータ
11 回転体
12 モータステータ
13 ロータアッセンブリ
14 永久磁石
15A 低圧段側軸受
15B 高圧段側軸受
16A 低圧段側軸受ハウジング
16B 高圧段側軸受ハウジング
17 ステータハウジング
18A 低圧段側スリーブ
18B 高圧段側スリーブ
19 与圧バネ
21 圧縮空気供給ライン
24,33,79,89,206,208 空間
25,38 隙間
26,29 圧縮空気導入ライン
27 サージタンク
28 圧縮機
30,57 背面
32 低圧段側面
34,181 外周面
36,165 内面
41,51 ハブ
43,53 インペラ翼
61 低圧段入口開口
62 低圧段出口開口
63,73 供給流路
64,74 スクロール流路
66 低圧段インペラ室
71 高圧段入口開口
72 高圧段出口開口
76 高圧段インペラ室
81 高圧段側接続部
82 低圧段側接続部
83 中間部
84 低圧段側湾曲部
85 高圧段側湾曲部
86,87,88,202,204 シール部材
90,91 圧縮空気供給孔
90a,91a,92a,93a 入口
90b,91b,92b,93b 出口
92,93 パージ孔
94,212 内輪
95,213 外輪
96,214 ボール
97,215 環状シール板
98,216 シール板隙間
100 リップシール
100a 基端部
100b 先端部
100c 第1接続部
100d 第2接続部
161,162 軸受支持面
164,166 係止面
165a 第1内面
165b 段差面
165c 第2内面
167 高圧段側面
168,170 外面
181a 大径部
181b 小径部
182,183,184,203,205 環状溝
211,264 分岐部
219 磁性体
220 電磁石
222 電源ユニット
224 回転数センサ
226 電源制御部
230 負圧ポンプ
232,234 パージライン
236 ポンプ制御部
261 第1配管
262 第2配管
263 切替装置
291 第3配管
292 減圧用絞り弁
CA (回転シャフトの)軸線
X 軸方向
XH (軸方向の)高圧段側
XL (軸方向の)低圧段側
Y 径方向
Claims (15)
- 回転シャフトを含む電動モータと、
前記回転シャフトの一端側に設けられた第1インペラと、
前記第1インペラと前記電動モータとの間の位置で前記回転シャフトを回転可能に支持し、潤滑剤を含む第1軸受と、
前記第1軸受を収容する第1軸受ハウジングと、
を備え、
前記第1軸受ハウジングは、前記回転シャフトを含む回転体と前記第1軸受ハウジングとの隙間に前記第1軸受ハウジングの外部から圧縮気体を供給するための圧縮気体供給孔を含み、
前記圧縮気体供給孔の出口は、前記第1軸受ハウジングの内面に設けられ、前記回転シャフトの軸方向における前記第1インペラと前記第1軸受との間に位置する、電動遠心圧縮機。 - 前記軸方向における前記第1インペラと前記圧縮気体供給孔の前記出口との間の位置において前記隙間をシールするように設けられた第1シール部材と、
前記軸方向における前記圧縮気体供給孔の前記出口と前記第1軸受との間の位置において前記隙間をシールするように設けられた第2シール部材と、
を更に備える、請求項1に記載の電動遠心圧縮機。 - 前記軸方向における前記第2シール部材と前記第1軸受との間の位置において前記隙間をシールするように設けられた第3シール部材を更に備える、請求項2に記載の電動遠心圧縮機。
- 前記隙間のうち前記第1シール部材と前記第2シール部材との間の空間の圧力が前記第1インペラの背面に隣接する空間の圧力よりも大きくなるように、前記圧縮気体供給孔の入口に前記圧縮気体を導入するように構成された圧縮気体導入ラインを更に備える、請求項2又は3に記載の電動遠心圧縮機。
- 前記軸方向における前記第2シール部材と前記第1軸受との間の位置において前記隙間をシールするように設けられたリップシールを更に備える、請求項2乃至4の何れか1項に記載の電動遠心圧縮機。
- 前記リップシールの基端部は前記第1軸受ハウジングに固定され、前記リップシールの先端部は前記回転体の外周面に当接可能に構成された、請求項5に記載の電動遠心圧縮機。
- 前記リップシールの先端部を前記回転体の外周面から離間させるための電磁石を更に備える、請求項6に記載の電動遠心圧縮機。
- 前記電磁石に電流を印加するように構成された電源ユニットと、
前記回転シャフトの回転数を計測するための回転数センサと、
前記電源ユニットを制御するための電源制御部と、
を備え、
前記電源制御部は、前記回転数センサによって計測した前記回転シャフトの回転数に基づいて、前記電磁石に電流を流すように構成された、請求項7に記載の電動遠心圧縮機。 - 前記電源制御部は、前記回転数センサによって計測した前記回転シャフトの回転数が基準値を超えた場合に、前記電磁石に電流を流して前記リップシールの前記先端部を前記回転体の外周面から離間させるように構成された、請求項8に記載の電動遠心圧縮機。
- 前記第1軸受ハウジングは、前記圧縮気体供給孔から前記隙間に供給された前記圧縮気体を前記隙間から前記第1軸受ハウジングの外部に排出するためのパージ孔を含み、
前記パージ孔の入口は、前記第1軸受ハウジングの内面に設けられ、前記軸方向における前記第1インペラと前記第1軸受との間に位置する、請求項2乃至9の何れか1項に記載の電動遠心圧縮機。 - 前記第1軸受は、内輪と、外輪と、前記内輪と外輪との間に保持された複数の転動体と、前記軸方向において前記転動体の両側にそれぞれ位置し、前記外輪に保持された一対の環状シール板と、を含み、
前記一対の環状シール板のうち前記第1インペラ側の環状シール板と前記内輪との間に形成される環状の隙間をシール板隙間と定義すると、
前記パージ孔の通路断面積は、前記シール板隙間の前記軸方向に直交する断面積よりも大きい、請求項10に記載の電動遠心圧縮機。 - 前記パージ孔から気体を吸い出すための負圧ポンプを更に備える、請求項10又は11に記載の電動遠心圧縮機。
- 前記負圧ポンプを制御するためのポンプ制御部を更に備え、
前記ポンプ制御部は、前記電動モータの停止時に前記負圧ポンプを作動させるように構成された、請求項12に記載の電動遠心圧縮機。 - 前記電動遠心圧縮機は、多段電動遠心圧縮機であり、
前記回転シャフトの他端側に設けられた第2インペラと、
前記第2インペラと前記電動モータとの間の位置で前記回転シャフトを回転可能に支持し、潤滑剤を含む第2軸受と、
前記第2軸受を収容する第2軸受ハウジングと、
を備え、
前記第2軸受ハウジングは、前記回転体と前記第2軸受ハウジングとの隙間に圧縮気体を供給するための圧縮気体供給孔を含み、
前記第2軸受ハウジングの前記圧縮気体供給孔の出口は、前記軸方向における前記第2インペラと前記第2軸受との間に位置する、請求項1乃至13の何れか1項に記載の電動遠心圧縮機。 - 前記第1インペラを収納する低圧段ハウジングと、
前記第2インペラを収納する高圧段ハウジングと、
前記第1インペラにより圧縮された圧縮気体を前記高圧段ハウジングに供給するためのつなぎ配管と、を備え、
前記高圧段ハウジングは、前記回転シャフトの軸線に対して交差する方向に向かって開口する高圧段入口開口を有し、
前記つなぎ配管は、前記高圧段入口開口に接続される、請求項14に記載の電動遠心圧縮機。
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JP2008057452A (ja) * | 2006-08-31 | 2008-03-13 | Hitachi Ltd | ヒートポンプシステム、ヒートポンプシステムの軸封方法 |
JP2012189009A (ja) * | 2011-03-11 | 2012-10-04 | Kobe Steel Ltd | 水噴射式スクリュ流体機械 |
US9605683B2 (en) * | 2013-05-30 | 2017-03-28 | Ingersoll-Rand Company | Centrifugal compressor having a bearing assembly |
JP2018123759A (ja) * | 2017-02-01 | 2018-08-09 | パナソニックIpマネジメント株式会社 | ターボ圧縮機 |
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US9709068B2 (en) | 2014-02-19 | 2017-07-18 | Honeywell International Inc. | Sealing arrangement for fuel cell compressor |
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JP2008057452A (ja) * | 2006-08-31 | 2008-03-13 | Hitachi Ltd | ヒートポンプシステム、ヒートポンプシステムの軸封方法 |
JP2012189009A (ja) * | 2011-03-11 | 2012-10-04 | Kobe Steel Ltd | 水噴射式スクリュ流体機械 |
US9605683B2 (en) * | 2013-05-30 | 2017-03-28 | Ingersoll-Rand Company | Centrifugal compressor having a bearing assembly |
JP2018123759A (ja) * | 2017-02-01 | 2018-08-09 | パナソニックIpマネジメント株式会社 | ターボ圧縮機 |
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