WO2022208839A1 - 過給機 - Google Patents
過給機 Download PDFInfo
- Publication number
- WO2022208839A1 WO2022208839A1 PCT/JP2021/014145 JP2021014145W WO2022208839A1 WO 2022208839 A1 WO2022208839 A1 WO 2022208839A1 JP 2021014145 W JP2021014145 W JP 2021014145W WO 2022208839 A1 WO2022208839 A1 WO 2022208839A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- lubricating oil
- bearing
- cooling space
- impeller
- space
- Prior art date
Links
- 239000010687 lubricating oil Substances 0.000 claims abstract description 142
- 238000001816 cooling Methods 0.000 claims abstract description 99
- 230000004308 accommodation Effects 0.000 abstract description 4
- 238000002485 combustion reaction Methods 0.000 description 34
- 239000007789 gas Substances 0.000 description 32
- NJPPVKZQTLUDBO-UHFFFAOYSA-N novaluron Chemical compound C1=C(Cl)C(OC(F)(F)C(OC(F)(F)F)F)=CC=C1NC(=O)NC(=O)C1=C(F)C=CC=C1F NJPPVKZQTLUDBO-UHFFFAOYSA-N 0.000 description 9
- 238000010586 diagram Methods 0.000 description 8
- 239000003921 oil Substances 0.000 description 8
- 230000002093 peripheral effect Effects 0.000 description 7
- 230000014509 gene expression Effects 0.000 description 5
- 238000011144 upstream manufacturing Methods 0.000 description 5
- 238000012986 modification Methods 0.000 description 4
- 230000004048 modification Effects 0.000 description 4
- 238000005192 partition Methods 0.000 description 4
- 239000000314 lubricant Substances 0.000 description 3
- 238000011084 recovery Methods 0.000 description 3
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000000567 combustion gas Substances 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/14—Lubrication of pumps; Safety measures therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/12—Cooling
- F01D25/125—Cooling of bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/005—Cooling of pump drives
-
- 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
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present disclosure relates to a supercharger with a centrifugal compressor.
- An internal combustion engine (for example, an engine) is sometimes equipped with a supercharger to improve its output.
- the turbocharger rotates a compressor impeller (hereinafter referred to as impeller) by rotating the turbine rotor with the exhaust gas from the internal combustion engine, and compresses the gas (for example, combustion air) supplied to the internal combustion engine.
- an exhaust turbine type turbocharger configured for As a compressor for an exhaust turbine supercharger, a centrifugal compressor is known that sends out the gas sent to the impeller outward in a radial direction perpendicular to the rotation axis of the impeller.
- JP 2014-111905 A Japanese Patent No. 6246847 Japanese Patent No. 3606293
- the impeller was cooled by supplying cooling air to the space facing the back of the compressor (see Patent Document 1, for example).
- Combustion air that has passed through an intercooler after being compressed by a centrifugal compressor has sometimes been used as the cooling air.
- part of the combustion air compressed by the centrifugal compressor is not supplied to the internal combustion engine, which may lead to a decrease in efficiency of the entire internal combustion engine system including the internal combustion engine.
- an object of at least one embodiment of the present disclosure is to provide a supercharger capable of cooling the back surface of the compressor impeller and improving the efficiency of the internal combustion engine system.
- the turbocharger is A turbocharger comprising a rotor including a compressor impeller, a bearing that rotatably supports the rotor, and a bearing base that houses the bearing,
- the bearing stand is a cooling space formed on the back side of the compressor impeller; a bearing housing space for housing the bearing; a lubricating oil flow path communicating between the cooling space and the bearing housing space for sending lubricating oil from the cooling space to the bearing housing space; a lubricating oil supply port formed on the outer surface of the housing, the lubricating oil supply port communicating with the cooling space;
- the turbocharger is It further comprises a lubricating oil supply line configured to send lubricating oil from the outside of the supercharger to the cooling space through the lubricating oil supply port.
- a turbocharger is provided that can cool the back surface of the compressor impeller and improve the efficiency of the internal combustion engine system.
- FIG. 1 is an explanatory diagram for explaining the configuration of an internal combustion engine system including a supercharger according to an embodiment of the present disclosure
- FIG. FIG. 2 is a schematic cross-sectional view of the turbocharger showing an A section extracted from the turbocharger shown in FIG. 1
- 1 is a schematic cross-sectional view of a turbocharger according to an embodiment of the present disclosure, showing a portion corresponding to a section A of the turbocharger shown in FIG. 1
- FIG. FIG. 3 is an explanatory diagram for explaining a lubricating oil system in the supercharger shown in FIG. 2
- FIG. 3 is an explanatory diagram for explaining a modification of the lubricating oil system in the supercharger shown in FIG. 2
- FIG. 4 is an explanatory diagram for explaining a lubricating oil system in the turbocharger shown in FIG. 3;
- 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 an explanatory diagram for explaining the configuration of an internal combustion engine system including a turbocharger according to one embodiment of the present disclosure.
- FIG. 2 is a schematic cross-sectional view of the turbocharger showing an A portion extracted from the turbocharger shown in FIG.
- FIG. 3 is a schematic cross-sectional view of a turbocharger according to an embodiment of the present disclosure, and is a schematic cross-sectional view of the turbocharger showing a portion corresponding to part A of the turbocharger shown in FIG. be.
- the up-down direction in the drawing corresponds to the vertical direction
- the upper side in the drawing corresponds to the upper direction in the vertical direction.
- a supercharger 10 is configured to rotatably support a rotor 3 including a compressor impeller 2 (hereinafter abbreviated as the impeller 2) and the rotor 3, as shown in FIG. and a bearing pedestal 7 configured to accommodate the bearing 4 .
- the turbocharger 10 is applied to a marine engine turbocharger, a land-use generator engine turbocharger, and the like.
- the turbocharger 10 can also be applied to a turbocharger for automobiles, which is smaller than a turbocharger for marine engines.
- the direction in which the axis CA of the supercharger 10 extends is defined as the axial direction X
- the direction orthogonal to the axis CA is defined as the radial direction Y.
- the side of the axial direction X where the intake port 61 is located with respect to the impeller 2 is defined as the front side XF
- the side opposite to the intake port 61 side is defined as the rear side XR.
- the rotor 3 comprises a rotating shaft 31 having a longitudinal direction along the axial direction X, an impeller 2 mechanically coupled to the front XF end 311 of the rotating shaft 31 , the rotating shaft 31 a turbine 32 mechanically coupled to the aft XR end 312 of the .
- the impeller 2 is arranged coaxially with the turbine 32 .
- the impeller 2, as shown in FIG. 1, is provided in a supply line 12 that supplies gas (eg, combustion gas such as air) to an internal combustion engine 11 (eg, engine).
- the turbine 32 is provided in an exhaust line 13 for exhausting exhaust gas from the internal combustion engine 11 .
- the internal combustion engine system 1 includes a supercharger 10 , an internal combustion engine 11 , a supply line 12 , an exhaust line 13 and an intercooler 14 .
- the supercharger 10 includes a compressor housing 6 configured to rotatably house the impeller 2 and a turbine housing 8 configured to rotatably house the turbine 32 .
- the bearing stand 7 is arranged between the compressor housing 6 and the turbine housing 8 and is mechanically connected to the compressor housing 6 and the turbine housing 8 by fastening members such as bolts.
- the turbocharger 10 rotates the turbine 32 by exhaust gas introduced into the turbine housing 8 through the exhaust line 13 from the internal combustion engine 11 . Since the impeller 2 is mechanically connected to the turbine 32 via the rotating shaft 31 , it rotates together with the rotation of the turbine 32 . By rotating the impeller 2 , the supercharger 10 compresses the gas introduced into the compressor housing 6 through the supply line 12 and sends the compressed gas to the internal combustion engine 11 . The gas compressed by the impeller 2 is supplied to the internal combustion engine 11 after being cooled by an intercooler 14 provided between the impeller 2 and the internal combustion engine 11 in the supply line 12 .
- the impeller 2 has a hub 21 and a plurality of impeller blades 23 provided on the outer surface 22 of the hub 21 .
- the hub 21 is mechanically fixed to the front XF end 311 of the rotating shaft 31 . Therefore, the hub 21 and the plurality of impeller blades 23 are rotatable around the axis CA of the supercharger 10 integrally with the rotary shaft 31 .
- the impeller 2 consists of a centrifugal impeller configured to direct the gas delivered from the front side XF in the axial direction X outward in the radial direction Y. As shown in FIG.
- the compressor housing 6 has an intake port 61 for introducing gas from the outside of the compressor housing 6, an exhaust port (not shown) for discharging the gas that has passed through the impeller to the outside of the compressor housing and sending it to the internal combustion engine, is formed.
- the turbine housing 8 includes an exhaust gas introduction port (not shown) for introducing exhaust gas into the turbine housing 8, an exhaust gas discharge port 81 for discharging the exhaust gas generated by rotating the turbine 32 to the outside of the turbine housing 8, is formed.
- the compressor housing 6 includes an air intake introduction portion 620 forming an air intake passage 62 for introducing gas introduced into the compressor housing 6 from the air intake port 61 into the impeller 2, A shroud portion 630 having a shroud surface 63 curved in a convex shape so as to face each other, and a scroll portion 640 forming a scroll flow path 64 for guiding the gas that has passed through the impeller 2 to the outside of the compressor housing 6 are provided.
- Each of the intake channel 62 and the scroll channel 64 is formed inside the compressor housing 6 .
- the compressor housing 6 includes an impeller chamber 65 that rotatably houses the impeller 2 and a diffuser passage 66 that guides gas from the impeller 2 to the scroll passage 64 in combination with the bearing pedestal 7 . and are formed.
- the shroud surface 63 described above defines the front XF portion of the impeller chamber 65 .
- FIGS. 1 to 3 when the impeller 2 is housed in the impeller chamber 65, there is a gap between the back surface 24 of the impeller 2 (surface on the rear side XR side) and the end surface 71 on the front side XF side of the bearing stand 7.
- a gap 65A is formed in .
- upstream side in the flow direction of the gas flowing inside the compressor housing 6 may be simply referred to as the "upstream side”
- downstream side in the flow direction of the gas may simply be referred to as the "downstream side”.
- the intake passage 62 extends along the axial direction X.
- the intake passage 62 communicates with the intake port 61 located on the front side XF (upstream side) and the inlet side of the impeller chamber 65 located on the rear side XR (downstream side).
- the diffuser flow path 66 extends along a direction intersecting (for example, perpendicular to) the axis CA of the supercharger 10 .
- the diffuser channel 66 communicates with the outlet side of the impeller chamber 65 located upstream and the scroll channel 64 located downstream.
- the scroll flow path 64 has a spiral shape surrounding the periphery of the impeller 2 (outside in the radial direction Y).
- the scroll flow path 64 communicates with a diffuser flow path 66 located upstream and a discharge port (not shown) located downstream.
- the gas introduced into the compressor housing 6 from the intake port 61 flows through the intake passage 62 along the axial direction X to the rear side XR, and then is sent to the impeller 2 and compressed by the impeller 2 .
- the gas compressed by the impeller 2 flows outward in the radial direction through the diffuser flow path 66 and the scroll flow path 64 in this order, and is then discharged to the outside of the compressor housing 6 from a discharge port (not shown). Part of the gas compressed by impeller 2 flows into gap 65A described above.
- a cooling space 72 in which lubricating oil flows as a cooling medium on the back surface 24 side of the impeller 2, and a bearing housing space for housing the bearing 4 described above. 73 and are formed.
- the cooling space 72 is formed on the front side XF of the bearing housing space 73, in other words, between the gap 65A and the bearing housing space 73 in the axial direction X.
- the cooling space 72 has a distance D1 to the gap 65A that is shorter than a distance D2 to the bearing accommodation space 73, as shown in FIG.
- the cooling space 72 extends along the circumferential direction around the axis CA of the supercharger 10 and is formed outside the bearing housing space 73 in the radial direction Y. As shown in FIG. In addition, the cooling space 72 has an outer peripheral end 721 located outside the trailing edge 25 of the impeller blades 23 in the radial direction Y, and an inner peripheral end 722 of the cooling space 72 located radially Y relative to the trailing edge 25 of the impeller blades 23 . located inside.
- the illustrated embodiment shows an example of a lubricating oil system in the turbocharger 10.
- the cooling space 72, the bearing housing space 73, and a lubricating oil supply passage 750, which will be described later, constitute the lubricating oil system. and the lubricating oil flow path 76 are not limited to the illustrated configuration.
- the bearing base 7 has at least one lubricating oil supply port 75 formed in an outer surface 74 exposed to the outside and communicating with the cooling space 72, the cooling space 72 and the bearing. At least one lubricating oil flow path 76 communicating with the housing space 73 is formed. At least one lubricating oil supply channel 750 for feeding lubricating oil to the cooling space 72 from the outside is formed inside the bearing stand 7 .
- a lubricating oil supply port 75 is formed on one end side of the lubricating oil supply channel 750 , and a communication port 723 communicating with the cooling space 72 is formed on the other end side of the lubricating oil supply channel 750 .
- the lubricating oil flow path 76 has an inlet opening 761 communicating with the cooling space 72 at one end thereof, and an outlet opening 762 communicating with the bearing housing space 73 at the other end thereof.
- the "outer surface 74 exposed to the outside" includes a surface accessible from the outside of the bearing base 7 in the turbocharger 10 after assembly, and the lubricating oil supply port 75 is formed in such a surface. may Also, in the illustrated example, the lubricating oil is supplied into the bearing pedestal 7 from above the bearing pedestal 7 , but it may be supplied into the bearing pedestal 7 from below the bearing pedestal 7 .
- the turbocharger 10 further includes a lubricating oil supply line 9 configured to send lubricating oil from the outside of the bearing stand 7 to the cooling space 72 through a lubricating oil supply port 75 .
- the lubricating oil supply line 9 includes at least a lubricating oil pipe 91 having one end connected to the lubricating oil supply port 75 and a lubricating oil pump 92 provided at the other end of the lubricating oil pipe 91 .
- the lubricating oil pump 92 is configured to generate power for pumping the lubricating oil by electric power.
- the lubricating oil is sent from the other end side of the lubricating oil pipe 91 to the one end side, and then sent to the cooling space 72 through the lubricating oil supply port 75 .
- the lubricating oil sent to the cooling space 72 cools the region 71A including the end surface 71 on the front side of the cooling space 72 in the bearing stand 7, thereby indirectly cooling the gas existing in the gap 65A. be.
- heat input from the gap 65A to the back surface 24 of the impeller 2 can be suppressed, thereby suppressing an increase in the metal temperature of the impeller 2 when the turbocharger 10 is driven.
- the lubricating oil in the cooling space 72 is sent to the bearing housing space 73 through the lubricating oil flow path 76 by the lubricating oil pump 92 and supplied to the bearings 4 housed in the bearing housing space 73 .
- the outlet opening 762 of the lubricating oil flow path 76 is formed in an inner wall surface 731A of the inner wall surface 731 that defines the bearing housing space 73 and faces the outer surface 41 of the bearing 4 .
- Lubricating oil is supplied to the bearing 4 from the outer surface 41 side of the bearing 4 .
- the lubricating oil in the cooling space 72 receives heat from the gas existing in the gap 65A, and its temperature rises, and its viscosity is lower than before the temperature rise.
- the lubricating oil with reduced viscosity is supplied to the bearings 4 , the friction caused by the viscous resistance of the lubricating oil can be reduced, so that the mechanical loss of the bearings 4 can be suppressed.
- the supercharger 10 includes the impeller 2 described above, the bearing stand 7 described above, and the lubricating oil supply line 9 described above.
- the bearing base 7 is formed with the cooling space 72 , the bearing housing space 73 , the lubricating oil supply port 75 and the lubricating oil flow path 76 described above.
- the centrifugal compressor of the supercharger 10 can be operated at a high pressure ratio.
- the lubricating oil whose temperature has been raised by receiving heat in the cooling space 72 flows through the lubricating oil flow path 76 into the bearing housing space 73 that houses the bearing 4 . Since the bearing 4 is supplied with the lubricating oil whose viscosity has decreased due to the temperature rise in the cooling space 72, the mechanical efficiency of the bearing 4 can be improved, and the internal combustion engine system 1 including the turbocharger 10 can be improved. Efficiency can be improved.
- the lubricating oil supply line 9 discussed above is a lubricating oil recovery line configured to send the lubricating oil sent to the bearings 4 discussed above to a lubricating oil pump 92, as shown in FIG. 93 is further included.
- the internal combustion engine system 1 is provided with the lubricating oil supply line 9 including the lubricating oil recovery line 93 , the lubricating oil can be circulated through the lubricating oil supply line 9 .
- the lubricating oil supply line 9 described above, as shown in FIG. further includes cooler 94 .
- the oil cooler 94 is configured to cool lubricating oil passing through the oil cooler 94 .
- the lubricating oil receives heat when circulating in the bearing stand 7 and raises its temperature. If the temperature of the lubricating oil sent to the cooling space 72 becomes too high, the cooling performance of the lubricating oil may deteriorate.
- the internal combustion engine system 1 including the turbocharger 10 and the internal combustion engine 11 has a lubricating oil circulation system that circulates lubricating oil.
- the oil cooler 94 described above the oil cooler used in the lubricating oil circulation system may be used. In this case, proper cooling of the back surface 24 of the impeller 2 can be achieved without significant modifications to the internal combustion engine system 1 .
- FIG. 4 is an explanatory diagram for explaining a lubricating oil system in the supercharger shown in FIG. 2.
- FIG. FIG. 5 is an explanatory diagram for explaining a modification of the lubricating oil system in the supercharger shown in FIG. FIGS. 4, 5, and 6, which will be described later, schematically show the lubricating oil system in the supercharger as seen from the front side in the axial direction.
- a lubricating oil system in the supercharger 10 includes a cooling space 72, a bearing housing space 73, a lubricating oil flow path 76, and the like.
- the cooling space 72 described above is formed in an annular shape extending along the circumferential direction of the supercharger 10, as shown in FIGS.
- the inner wall surface 720 defining the cooling space 72 is formed with at least one communication port 723 and at least one inlet opening 761 described above.
- At least one communication port 723 includes a communication port 723A communicating with one of two lubricating oil supply ports 75 formed in the bearing base 7, and two lubricating oil supply ports 723A. and a communication port 723B communicating with the other of the ports 75.
- the two communication ports 723A and 723B are formed in the upper part of the inner wall surface 720 and are formed at positions apart from each other in the circumferential direction of the supercharger 10 .
- One communication port 723A is provided on one side (for example, the left side in the figure) in the width direction (the direction orthogonal to the direction in which the axis CA of the supercharger 10 extends and the vertical direction), and the other communication port 723B is provided on the other side in the width direction (for example, the right side in the figure). Also, an inlet opening 761 is formed in the lower portion of the inner wall surface 720 .
- the lubricating oil that has flowed into the cooling space 72 from one communication port 723A flows downward on one side of the cooling space 72 in the width direction, and then flows out from the inlet opening 761 into the lubricating oil flow path 76 .
- the lubricating oil that has flowed into the cooling space 72 from the other communication port 723B flows downward on the other side of the cooling space 72 in the width direction, and then enters the lubricating oil flow path 76 from the inlet opening 761. leak.
- the lubricating oil that fills substantially the entire circumference of the annular cooling space 72 in the circumferential direction can cool the gas present in the gap 65A.
- the at least one communication port 723 includes one communication port 723C formed in the upper portion of the inner wall surface 720. Also, an inlet opening 761 is formed in the upper portion of the inner wall surface 720 .
- the communication port 723 ⁇ /b>C and the inlet opening 761 are formed at positions separated from each other in the circumferential direction of the supercharger 10 .
- the communication port 723C is provided on one side in the width direction (for example, the left side in the drawing), and the inlet opening 761 is provided on the other side in the width direction (for example, the right side in the drawing).
- the bearing pedestal 7 has a partition wall 79 that closes part of the cooling space 72 in the circumferential direction.
- the partition wall 79 is provided in the upper part of the cooling space 72 on the side where the interval between the communication port 723C and the inlet opening 761 in the circumferential direction of the cooling space 72 is narrow.
- the lubricating oil that has flowed into the cooling space 72 from the communication port 723C flows along the circumferential direction opposite to the side where the partition wall 79 is arranged (the lower part of the cooling space 72), and then flows through the inlet opening 761. It flows out to the lubricating oil flow path 76 .
- the lubricating oil is filled substantially over the entire circumference of the cooling space 72 in the circumferential direction.
- Appropriate cooling can be provided all around in the direction.
- the impeller 2 can be cooled more efficiently than when the cooling space 72 is partially formed in the circumferential direction.
- FIG. 6 is an explanatory diagram for explaining a lubricating oil system in the turbocharger shown in FIG. 3.
- the cooling space 72 described above is located above the axis CA of the supercharger 10, as shown in FIGS.
- the cooling space 72 is curved in an upwardly convex arc.
- the cooling space 72 is not formed below the axis CA of the supercharger 10 .
- At least one communication port 723 includes a communication port 723D formed in the upper portion of the inner wall surface 720.
- FIG. Inlet openings 761 of the two lubricating oil flow paths 76 are respectively formed below the communication port 723D of the inner wall surface 720 .
- the two inlet openings 761 are respectively formed at the tip (lower end) of the cooling space 72 curved in an arc shape.
- One of the two inlet openings 761 is provided on one side in the width direction (for example, the right side in the drawing), and the other of the two inlet openings 761 is provided on the other side in the width direction (for example, in the drawing). left).
- the two lubricating oil flow paths 76 may be provided completely independently, or may be joined in the middle.
- the lubricating oil whose temperature has risen in the cooling space 72 has a lower viscosity, and thus its fluidity is improved.
- the cooling space 72 since the cooling space 72 is positioned above the axis CA of the supercharger 10, the lubricating oil flows through the lubricating oil passage 76 into the region including the axis CA of the supercharger 10. It can easily flow into the formed bearing housing space 73 by its own weight.
- the flow distance of the lubricating oil in the cooling space 72 can be shortened compared to the case where the cooling space 72 is formed in an annular shape.
- the capacity of the lubricating oil pump 92 for feeding the lubricating oil can be reduced, so the manufacturing cost of the internal combustion engine system 1 can be reduced.
- the cooling space 72 formed in a part of the circumferential direction covers a part of the gap 65A facing the back surface 24 of the impeller 2 in the circumferential direction. By cooling, the back surface 24 of the impeller 2 can be cooled over the entire circumference.
- a turbocharger (10) according to at least one embodiment of the present disclosure, A turbocharger comprising a rotor (3) including a compressor impeller (2), a bearing (4) rotatably supporting the rotor (3), and a bearing stand (7) accommodating the bearing (4).
- the bearing pedestal (7) is a cooling space (72) formed on the back surface (24) side of the compressor impeller (2); a bearing housing space (73) for housing the bearing (4); a lubricating oil flow path (76) communicating the cooling space (72) and the bearing housing space (73) to send lubricating oil from the cooling space (72) to the bearing housing space (73); a lubricating oil supply port (75) formed in the outer surface (74) of the bearing stand (7), the lubricating oil supply port (75) communicating with the cooling space (72);
- the supercharger (10) is It further comprises a lubricating oil supply line (9) configured to send lubricating oil from the outside of the supercharger (10) to the cooling space (72) through the lubricating oil supply port (75).
- the back surface (24) of the impeller (2) is cooled by the lubricating oil sent to the cooling space (72) through the lubricating oil supply port (75) by the lubricating oil supply line (9). By doing so, the temperature rise of the impeller (2) can be suppressed. By suppressing the temperature rise of the impeller (2), the centrifugal compressor of the turbocharger (10) can be operated at a high pressure ratio.
- the lubricating oil whose temperature has been increased by receiving heat in the cooling space (72) passes through the lubricating oil flow path (76) to the bearing housing space (73) in which the bearing (4) is housed.
- the mechanical efficiency of the bearing (4) can be improved, which in turn leads to the supercharger (10). ), the efficiency of the internal combustion engine system (1) can be improved.
- the cooling space (72) is filled with the lubricating oil almost all around in the circumferential direction.
- the rear surface (24) of (2) can be appropriately cooled over the entire circumference. In this case, the impeller (2) can be cooled more efficiently than when the cooling space (72) is partially formed in the circumferential direction.
- turbocharger (10) of 1) above The cooling space (72) is located above the axis (CA) of the supercharger (10).
- the lubricating oil whose temperature has risen in the cooling space (72) has a lower viscosity, and thus its fluidity is improved.
- the cooling space (72) is positioned above the axis (CA) of the supercharger (10)
- the lubricating oil flows through the lubricating oil passage (76). It can easily flow into the bearing housing space (73) formed in the area including the axis (CA) of the feeder (10) by its own weight.
- the flow distance of the lubricating oil in the cooling space (72) can be shortened compared to the case where the cooling space (72) is formed in an annular shape.
- the capacity of the lubricating oil pump (92) for sending lubricating oil can be reduced, so that the manufacturing cost of the internal combustion engine system (1) can be reduced.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Supercharger (AREA)
Abstract
Description
コンプレッサインペラを含むロータと、前記ロータを回転可能に支持する軸受と、前記軸受を収容する軸受台と、を備える過給機であって、
前記軸受台は、
前記コンプレッサインペラの背面側に形成される冷却空間と、
前記軸受を収容する軸受収容空間と、
前記冷却空間から前記軸受収容空間に潤滑油を送るために、前記冷却空間と前記軸受収容空間とを連通させる潤滑油流路と、
前記ハウジングの外面に形成された潤滑油供給口であって、前記冷却空間に連通する潤滑油供給口と、が形成され、
前記過給機は、
前記潤滑油供給口を通じて前記過給機の外部から前記冷却空間に潤滑油を送るように構成された潤滑油供給ラインをさらに備える。
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過給機を備える内燃機関システムの構成を説明するための説明図である。図2は、図1に示される過給機のA部を抜き出して示す過給機の概略断面図である。図3は、本開示の一実施形態にかかる過給機の概略断面図であって、図1に示される過給機のA部に相当する部分を抜き出して示す過給機の概略断面図である。図1および後述する図2~6の夫々は、図中上下方向が鉛直方向に相当し、図中上方が鉛直方向における上方に相当している。
幾つかの実施形態にかかる過給機10は、図1に示されるように、コンプレッサインペラ2(以下、インペラ2と略す)を含むロータ3と、ロータ3を回転可能に支持するように構成された軸受4と、軸受4を収容するように構成された軸受台7と、を備える。過給機10は、舶用エンジン向けの過給機や、陸用の発電用エンジン向けの過給機などに適用されるものである。なお、過給機10は、舶用エンジン向けの過給機に比べて小型である自動車用の過給機にも適用可能である。
図示される実施形態では、冷却空間72は、図1に示されるように、隙間65Aとの間の距離D1が軸受収容空間73との間の距離D2よりも短い。冷却空間72は、過給機10の軸線CA周りの周方向に沿って延在するとともに、軸受収容空間73よりも径方向Yにおける外側に形成されている。また、冷却空間72は、その外周端721がインペラ翼23の後縁25よりも径方向Yにおける外側に位置するとともに、その内周端722がインペラ翼23の後縁25よりも径方向Yにおける内側に位置している。なお、図示される実施形態は、過給機10内の潤滑油系統の一例を示すものであり、この潤滑油系統を構成する冷却空間72、軸受収容空間73、後述する潤滑油供給流路750および潤滑油流路76などは、図示される構成に限定されるわけではない。
幾つかの実施形態では、上述した冷却空間72は、図4、5に示されるように、過給機10の周方向に沿って延在する環状に形成されている。冷却空間72を画定する内壁面720には、上述した少なくとも一つの連通口723と、上述した少なくとも一つの入口開口761と、が形成されている。
幾つかの実施形態では、上述した冷却空間72は、図3、6に示されるように、過給機10の軸線CAよりも上方に位置している。
例えば、図示される実施形態では、図6に示されるように、冷却空間72は、上方に凸となる円弧状に湾曲している。冷却空間72は、過給機10の軸線CAよりも下方には形成されていない。少なくとも一つの連通口723は、内壁面720の上部に形成される連通口723Dを含む。また、内壁面720の連通口723Dよりも下方には、二つの潤滑油流路76の入口開口761がそれぞれ形成されている。二つの入口開口761の夫々は、円弧状に湾曲した冷却空間72の先端部(下端部)の夫々に形成されている。二つの入口開口761のうちの一方は、上記幅方向における一方側(例えば、図中右側)に設けられ、二つの入口開口761のうちの他方は、上記幅方向における他方側(例えば、図中左側)に設けられる。なお、二つの潤滑油流路76は、完全に独立して設けられていてもよいし、途中で合流するようにしてもよい。
コンプレッサインペラ(2)を含むロータ(3)と、前記ロータ(3)を回転可能に支持する軸受(4)と、前記軸受(4)を収容する軸受台(7)と、を備える過給機(10)であって、
前記軸受台(7)は、
前記コンプレッサインペラ(2)の背面(24)側に形成される冷却空間(72)と、
前記軸受(4)を収容する軸受収容空間(73)と、
前記冷却空間(72)から前記軸受収容空間(73)に潤滑油を送るために、前記冷却空間(72)と前記軸受収容空間(73)とを連通させる潤滑油流路(76)と、
前記軸受台(7)の外面(74)に形成された潤滑油供給口(75)であって、前記冷却空間(72)に連通する潤滑油供給口(75)と、が形成され、
前記過給機(10)は、
前記潤滑油供給口(75)を通じて前記過給機(10)の外部から前記冷却空間(72)に潤滑油を送るように構成された潤滑油供給ライン(9)をさらに備える。
前記冷却空間(72)は、前記ロータ(3)の周方向に沿って延在する環状に形成された。
前記冷却空間(72)は、前記過給機(10)の軸線(CA)よりも上方に位置している。
2 インペラ
21 ハブ
22 外表面
23 インペラ翼
231 先端
24 背面
25 後縁
3 ロータ
31 回転シャフト
311 前側の端部
312 後側の端部
32 タービン
4 軸受
41 外表面
6 コンプレッサハウジング
61 吸気口
62 吸気流路
620 吸気導入部
63 シュラウド面
630 シュラウド部
64 スクロール流路
640 スクロール部
65 インペラ室
65A 隙間
66 ディフューザ流路
7 軸受台
71 端面
71A 領域
72 冷却空間
720 内壁面
721 外周端
722 内周端
723,723A~723D 連通口
73 軸受収容空間
731,731A 内壁面
74 外面
75 潤滑油供給口
750 潤滑油供給流路
76 潤滑油流路
761 入口開口
762 出口開口
79 隔壁
8 タービンハウジング
81 排ガス排出口
9 潤滑油供給ライン
91 潤滑油配管
92 潤滑油ポンプ
93 潤滑油回収ライン
94 オイルクーラ
10 過給機
11 内燃機関
12 供給ライン
13 排出ライン
14 中間冷却器
CA 軸線
X 軸方向
XF (軸方向の)前側
XR (軸方向の)後側
Y 径方向
Claims (3)
- コンプレッサインペラを含むロータと、前記ロータを回転可能に支持する軸受と、前記軸受を収容する軸受台と、を備える過給機であって、
前記軸受台は、
前記コンプレッサインペラの背面側に形成される冷却空間と、
前記軸受を収容する軸受収容空間と、
前記冷却空間から前記軸受収容空間に潤滑油を送るために、前記冷却空間と前記軸受収容空間とを連通させる潤滑油流路と、
前記軸受台の外面に形成された潤滑油供給口であって、前記冷却空間に連通する潤滑油供給口と、が形成され、
前記過給機は、
前記潤滑油供給口を通じて前記過給機の外部から前記冷却空間に潤滑油を送るように構成された潤滑油供給ラインをさらに備える、
過給機。 - 前記冷却空間は、前記ロータの周方向に沿って延在する環状に形成された、
請求項1に記載の過給機。 - 前記冷却空間は、前記過給機の軸線よりも上方に位置している、
請求項1に記載の過給機。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2021/014145 WO2022208839A1 (ja) | 2021-04-01 | 2021-04-01 | 過給機 |
CN202180096311.0A CN117083451A (zh) | 2021-04-01 | 2021-04-01 | 增压器 |
KR1020237028796A KR20230131946A (ko) | 2021-04-01 | 2021-04-01 | 과급기 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2021/014145 WO2022208839A1 (ja) | 2021-04-01 | 2021-04-01 | 過給機 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2022208839A1 true WO2022208839A1 (ja) | 2022-10-06 |
Family
ID=83458281
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2021/014145 WO2022208839A1 (ja) | 2021-04-01 | 2021-04-01 | 過給機 |
Country Status (3)
Country | Link |
---|---|
KR (1) | KR20230131946A (ja) |
CN (1) | CN117083451A (ja) |
WO (1) | WO2022208839A1 (ja) |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01178723A (ja) * | 1987-12-29 | 1989-07-14 | Yanmar Diesel Engine Co Ltd | ターボチャージャーの冷却構造 |
JP2016075183A (ja) * | 2014-10-03 | 2016-05-12 | 三菱重工業株式会社 | 過給機 |
JP2017053300A (ja) * | 2015-09-11 | 2017-03-16 | 株式会社豊田自動織機 | エンジンの過給装置 |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS606293B2 (ja) | 1977-08-26 | 1985-02-16 | 住友電気工業株式会社 | 光伝送用ガラスフアイバ−素材の製造方法 |
JPS6246847U (ja) | 1985-09-10 | 1987-03-23 | ||
JP2014111905A (ja) | 2012-12-05 | 2014-06-19 | Mitsubishi Heavy Ind Ltd | 遠心圧縮機およびこれを備えた過給機ならびに遠心圧縮機の運転方法 |
-
2021
- 2021-04-01 CN CN202180096311.0A patent/CN117083451A/zh active Pending
- 2021-04-01 KR KR1020237028796A patent/KR20230131946A/ko active Search and Examination
- 2021-04-01 WO PCT/JP2021/014145 patent/WO2022208839A1/ja active Application Filing
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01178723A (ja) * | 1987-12-29 | 1989-07-14 | Yanmar Diesel Engine Co Ltd | ターボチャージャーの冷却構造 |
JP2016075183A (ja) * | 2014-10-03 | 2016-05-12 | 三菱重工業株式会社 | 過給機 |
JP2017053300A (ja) * | 2015-09-11 | 2017-03-16 | 株式会社豊田自動織機 | エンジンの過給装置 |
Also Published As
Publication number | Publication date |
---|---|
CN117083451A (zh) | 2023-11-17 |
KR20230131946A (ko) | 2023-09-14 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1092085B1 (en) | Low speed high pressure ratio turbocharger | |
CN101573516B (zh) | 排气涡轮增压器 | |
US8834032B2 (en) | Tilting pad journal bearing and rotating machine provided with the same | |
US20090056681A1 (en) | Supercharger with electric motor | |
JP6399894B2 (ja) | 排気装置及びガスタービン | |
KR20180037072A (ko) | 과급기 및 모터 냉각 방법 | |
JP2011512479A (ja) | 羽根車およびターボチャージャー | |
KR20150081342A (ko) | 원심압축기 및 이를 구비한 과급기 및 원심압축기의 운전방법 | |
KR20140066105A (ko) | 구동 어셈블리의 과급 장치 | |
KR20180124402A (ko) | 터보 압축기 | |
JP6682374B2 (ja) | 電動過給圧縮機 | |
CN107849973B (zh) | 叶轮背面冷却结构以及增压器 | |
CN113482973A (zh) | 具有在轴向热交换器装置中的冷却空气通道和液体冷却剂通道的压缩机 | |
JP7105823B2 (ja) | 過給機 | |
WO2022208839A1 (ja) | 過給機 | |
CN110344927B (zh) | 内燃机 | |
US10738795B2 (en) | Turbocharger with thermo-decoupled wheel contour inlet for water-cooled compressor housing | |
US11339663B2 (en) | Rotor having improved structure, and turbine and gas turbine including the same | |
CN113339287B (zh) | 涡轮压缩机 | |
WO2019142383A1 (ja) | ティルティングパッド軸受装置及び回転機械 | |
CN212615553U (zh) | 轴承壳体、壳体组件和涡轮增压器 | |
JP7183303B2 (ja) | ターボチャージャ | |
KR100923186B1 (ko) | 전동기 부착 과급기 | |
US11391177B2 (en) | Turbocharger | |
JP7455706B2 (ja) | ポンプ装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 21935001 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 20237028796 Country of ref document: KR Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1020237028796 Country of ref document: KR |
|
WWE | Wipo information: entry into national phase |
Ref document number: 202180096311.0 Country of ref document: CN |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 21935001 Country of ref document: EP Kind code of ref document: A1 |
|
NENP | Non-entry into the national phase |
Ref country code: JP |