WO2006043556A1 - ターボ機械、ターボ機械に用いられるコンプレッサインペラ、及びターボ機械の製造方法 - Google Patents
ターボ機械、ターボ機械に用いられるコンプレッサインペラ、及びターボ機械の製造方法 Download PDFInfo
- Publication number
- WO2006043556A1 WO2006043556A1 PCT/JP2005/019126 JP2005019126W WO2006043556A1 WO 2006043556 A1 WO2006043556 A1 WO 2006043556A1 JP 2005019126 W JP2005019126 W JP 2005019126W WO 2006043556 A1 WO2006043556 A1 WO 2006043556A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- drive shaft
- compressor impeller
- turbo machine
- turbomachine
- sleeve
- Prior art date
Links
Classifications
-
- 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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/026—Shaft to shaft connections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/025—Fixing blade carrying members on shafts
-
- 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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/027—Arrangements for balancing
-
- 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
- F04D25/04—Units comprising pumps and their driving means the pump being fluid-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
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/266—Rotors specially for elastic fluids mounting compressor rotors on shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2300/00—Materials; Properties thereof
- F05D2300/50—Intrinsic material properties or characteristics
- F05D2300/502—Thermal properties
- F05D2300/5021—Expansivity
- F05D2300/50212—Expansivity dissimilar
Definitions
- Turbomachine compressor impeller used in turbomachine, and method of manufacturing turbomachine
- the present invention relates to a turbomachine, a compressor impeller used for the turbomachine, and a method for manufacturing the turbomachine.
- a compressor impeller of a turbomachine represented by a turbocharger has been fixed to a drive shaft provided integrally with a turbine bin by a nut.
- the compressor blade is provided with a through-hole penetrating in the axial direction.
- the drive shaft is passed through the through-hole, and a nut is screwed into the threaded portion engraved on the tip side of the drive shaft. They were tightened and fixed.
- Patent Document 1 Japanese Patent Publication No. 5-504178
- Patent Document 2 US Pat. No. 5,193,989
- An object of the present invention is to provide a turbo machine capable of maintaining a good coupling state between a compressor impeller and a drive shaft, a compressor impeller used in the turbo machine, and a method of manufacturing the turbo machine.
- a turbomachine according to a first invention is
- a compressor impeller having a protrusion in the center of the back
- a drive shaft that fits into a bottomed coupling hole provided in the protrusion of the compressor impeller
- a cylindrical member fitted concentrically with the drive shaft is provided on the outer peripheral portion of the protrusion corresponding to the fitting portion of the drive shaft.
- a turbomachine according to a second invention is the first invention
- the fitting between the bottomed coupling hole of the protrusion and the drive shaft is an interference fit defined in JIS B 0401,
- the fitting between the protrusion and the tubular member is an intermediate fit or a gap fit as defined in JIS B 0401.
- the interference fit can be realized by fitting a shaft having a diameter about 10% larger than the hole diameter into the bottomed hole by press fitting, strong press fitting, shrink fitting, cold fitting, or the like. it can.
- the intermediate fitting can be realized by fitting the cylindrical member to the protruding portion by sliding, pushing, driving or the like.
- a turbomachine according to a third invention is the first invention or the second invention
- the cylindrical member is formed of a material having a smaller linear expansion coefficient than the compressor impeller.
- the cylindrical member for example, carbon steel (linear expansion coefficient: 10.1 to 12.1 X 10 _6 1 / ° C), chromium steel (linear thermal expansion coefficient: 9.5 to: L) I. 3 X 10 _6 1 / ° C), nickel steel (coefficient of linear thermal expansion: can be employed 18. OX 10 _6 lZ ° C) and the like.
- a turbomachine according to a fourth invention is any one of the first to third inventions, wherein the drive shaft is provided with a stepped shoulder,
- a sleeve inserted into the drive shaft is sandwiched between the shoulder and the compressor impeller.
- a turbomachine is provided.
- the sleeve is sandwiched between a shoulder portion of the drive shaft and the compressor impeller while receiving a surface pressure in an axial direction.
- a turbomachine according to a sixth invention is the fourth invention or the fifth invention.
- the sleeve is provided with the cylindrical member on the body.
- a turbomachine according to a seventh invention is any one of the fourth invention to the sixth invention, A housing for rotatably holding the drive shaft;
- a thrust collar fixed to the drive shaft
- a turbomachine according to an eighth aspect of the invention is the seventh aspect of the invention.
- the sleeve is provided with seal means for sealing lubricating oil and high-pressure air with the housing.
- a turbomachine according to a ninth invention is the same as the fourth invention, but the eighth invention,
- the sleeve and the drive shaft are provided with first slip restraining means for restraining slippage in the rotational direction by engaging with each other.
- a turbo machine is the turbomachine according to any one of the first to ninth aspects, wherein the annular member and the compressor impeller are engaged with each other to prevent slippage in the rotational direction. 2 is provided with slip prevention means.
- a turbomachine according to an eleventh aspect of the present invention is the turbomachinery according to any one of the first to tenth aspects of the present invention, wherein the compressor impeller and the drive shaft are engaged with each other to prevent slippage in the rotational direction. 3 is provided with slip prevention means.
- the turbo machine according to the twelfth aspect of the invention is the first invention! / And the eleventh aspect of the invention,
- the detaching means is provided on the side opposite to the protrusion of the compressor sine impeller along the drive shaft coupled to the compressor impeller, for example, by means of a female screw hole shape, a male screw shape, and a boss. Means can be configured.
- a compressor impeller according to a thirteenth aspect of the present invention is a compressor impeller used in a turbomachine, and has a cylindrical protrusion protruding from the back center force, and an inner peripheral portion and an outer peripheral portion of the protrusion are respectively
- the first connecting portion and the second connecting portion to be incorporated in the turbo machine are characterized in that [0020]
- a method of manufacturing a turbomachine according to a fourteenth invention is
- a compressor impeller having a protrusion in the center of the back
- a drive shaft that fits into a bottomed coupling hole provided in the protrusion of the compressor impeller
- a housing that rotatably supports the drive shaft
- a turbomachine manufacturing method comprising: a cylindrical member fitted concentrically with the drive shaft on an outer peripheral portion of the protrusion according to the fitting portion of the drive shaft;
- the force with which the drive shaft is fitted to the projection of the compressor impeller since the cylindrical member is fitted to the outer periphery of the projection, even if the drive shaft and compressor impeller become hot due to the drive, and the compressor impeller expands and the drive shaft is loosened, the cylindrical member on the outer peripheral side is strengthened and driven from the protrusion of the compressor impeller.
- the shaft can be prevented from coming off easily, and the durability can be surely improved.
- the fitting between the bottomed coupling hole of the protrusion and the drive shaft is an interference fit
- the engagement between the protrusion and the tubular member is an intermediate fit or a gap fit.
- the cylindrical member is formed of a material having a smaller linear expansion coefficient than that of the compressor impeller, so that even if the compressor impeller expands at a high temperature, the tubular member is accompanied by the high temperature of the cylindrical member. Since the expansion is smaller than that of the compressor impeller, the fitting at the outer periphery becomes tighter, and the fitting of the drive shaft and the compressor impeller can be firmly maintained.
- the compressor impeller and the sleeve are connected to the drive shaft at an appropriate axial position. Can be placed in a place.
- the sleeve since the sleeve is sandwiched between the compressor impeller and the shoulder while receiving the surface pressure, the sleeve can be reliably rotated together with the drive shaft.
- the cylindrical member cover is provided integrally with the sleeve, the number of members and the number of assembling steps can be reduced.
- the thrust bearing force sleeve and the thrust collar are sandwiched, it is possible to reliably prevent the drive shaft from being displaced in the axial direction via the sleeve and the thrust collar. Also, since the thrust bearing is sandwiched between two parts, an annular thrust bearing is used, unlike a structure in which a groove along the circumferential direction is provided in the sleeve and a horseshoe-shaped thrust bearing is placed in this groove. Can support the rotating surface in a well-balanced manner.
- the sleeve is provided with the sealing means for sealing the lubricating oil and the high-pressure air, so that the high-pressure air supply on the compressor impeller side enters the lubricating portion of the drive shaft. There is no need to worry if it leaks or the lubricating oil in the lubrication part leaks to the supercharged air side and mixes.
- the sleeve and the drive shaft are provided with the first slip suppression means, the sleeve and the drive shaft can be rotated together, and seizure or the like occurs between them. Can be prevented.
- the cylindrical member and the compressor impeller are provided with the second slip suppression means, and the compressor impeller and the drive shaft are provided with the third slip suppression means.
- the load on the coupling surface can be reduced compared to the case where the coupling is performed only by fitting each other, and it is possible to reliably resist slipping.
- the compressor impeller by providing the compressor impeller with the detachable means, it is possible to easily separate the fitting portion between the compressor impeller and the drive shaft using the detachable means, so that repair at the time of failure is also easily performed. be able to.
- the compressor impeller is incorporated into the turbomachine using both the outer peripheral portion and the inner peripheral portion of the protrusion, the compressor impeller is conventionally connected using the inner peripheral portion. Compared with this, the bond strength can be increased and the durability can be improved.
- the cylindrical member is inserted into the drive shaft, and press-fitting into the coupling hole of the compressor impeller and press-fitting into the protrusion of the cylindrical member are sequentially performed. Therefore, the work is easy and the installation time can be shortened.
- FIG. 1 is a cross-sectional view showing a turbo machine according to a first embodiment of the present invention.
- FIG. 2 is a cross-sectional view showing the main part of the turbomachine.
- FIG. 3 is a cross-sectional view of a coupling portion according to a second embodiment of the present invention.
- FIG. 4 is a front view of the drive shaft of the present embodiment.
- FIG. 5 is a front view of the sleeve of the present embodiment.
- FIG. 6 is a front view of the compressor impeller of the present embodiment.
- FIG. 7A is a cross-sectional view taken along the line AA in FIG. 7B of the joint portion according to the third embodiment of the present invention.
- FIG. 7B is a side view of the drive shaft of the present embodiment.
- FIG. 8A is a side sectional view of the sleeve of the present embodiment.
- FIG. 8B is a rear view of the sleeve according to the present embodiment.
- FIG. 1 is a sectional view showing a turbocharger (turbo machine) 1 according to a first embodiment of the present invention.
- FIG. 2 is a cross-sectional view showing the main part of the turbocharger 1.
- the turbocharger 1 is mounted on, for example, a gasoline engine or a diesel engine, and is not shown, and is a compressor 11 connected in the middle of an intake pipe to the engine.
- the compressor 11 including the exhaust turbine 12 connected in the middle of the exhaust pipe has a compressor impeller 13 that compresses intake air from the outside by rotating.
- the compressor impeller 13 is configured by attaching a plurality of blades arranged in the rotational direction to a hub having a substantially circular shape when viewed from the front, with a force not shown, and is formed of a forged product made of an aluminum alloy.
- a substantially central portion of the compressor impeller 13 protrudes in a mountain shape, and a female screw hole 131 as a detaching means is formed in a flat portion at the tip.
- This female screw hole 131 is used when the compressor impeller 13 and the drive shaft 15 are fitted again by the manufacturing procedure described later and then separated again.
- the female screw hole 131 is not shown in the figure. It is provided to facilitate separation when the removal tool is screwed and pulled out.
- the exhaust turbine 12 has a turbine wheel 14 that is rotated by inflowing exhaust gas.
- a steel drive shaft 15 is integrally formed on the turbine wheel 14 by friction welding, TIG welding, MIG welding, or the like. Has been.
- the drive shaft 15 is rotatably supported by a full float bearing 17 provided in the housing 16, and a compressor impeller 13 is coupled to the front end side of the drive shaft 15.
- a projection 19 projecting toward the turbine wheel 14 is provided at the center on the back side of the compressor impeller 13, that is, the center on the side facing the turbine wheel 14.
- the projection 19 is provided with a coupling hole 20 in the axial direction on the back side.
- the coupling hole 20 is a bottomed hole that is not a conventional through-hole penetrating the force compressor impeller 13 which is a hole for inserting and coupling the drive shaft 15.
- An inner peripheral portion of the coupling hole 20 is a first coupling portion 20A to which the drive shaft 15 is coupled.
- the drive shaft 15 At the front end side of the drive shaft 15, it is inserted into the coupling hole 20 of the compressor impeller 13 and its first end. 1 is provided with a fitting shaft portion 15A that is fitted to the coupling portion 20A, and a insertion portion 15B into which the sleeve 30 is inserted is provided on the proximal side of the fitting shaft portion 15A.
- the fitting state between the fitting shaft portion 15A and the first coupling portion 20A is a hole-based interference fitting (in the fitting symbol according to JIS, for example, H6Zu6).
- the compressor impeller 13 and the drive shaft 15 which have no conventional screw fastening structure are connected only by fitting.
- the sleeve 30 also has a substantially cylindrical body force with an open surface on the compressor impeller 13 side, and is made of steel having a smaller linear expansion coefficient than the aluminum compressor impeller 13.
- the sleeve 30 is provided with a through hole 30A into which the drive shaft 15 is inserted, and a fitting hole 33A communicating with the through hole 30A is provided on the compressor impeller 13 side of the through hole 30A.
- a cylindrical portion (cylindrical member) 33 is provided on the body.
- the fitting hole 33A of the cylindrical portion 33 is adapted to be fitted with the protrusion 19 of the compressor impeller 13 having a diameter larger than that of the through hole 30A. That is, the outer peripheral portion of the protrusion 19 to be inserted is a second coupling portion 19A coupled to the fitting hole 33A.
- the fitting state of the fitting hole 33A and the second coupling part 19A is a hole-based gap fitting or intermediate fitting.
- the fitting symbol by CFIS for example, H6Zh6, H6 / k6
- fitting The fitting between the shaft portion 15A and the first coupling portion 20A is set to be tighter.
- the concentricity of the drive shaft 15 and the compressor impeller 13 is reliably ensured without being affected by the fitting between the fitting hole 33A and the second coupling portion 19A.
- the compressor impeller 13 and the cylindrical portion 33 (sleeve 30), which have a structure such as screwing, are connected only by fitting.
- the cylindrical portion 33 having a smaller linear expansion coefficient than the compressor impeller 13 is fitted to the second coupling portion 19A of the projection portion 19, so that the drive shaft 15 is a compressor. Even if the impeller 13 reaches a high temperature and the compressor impeller 13 side is further thermally expanded to increase the diameter of the coupling hole 20, the expansion can be suppressed by the cylindrical portion 33, and the drive shaft 15 comes off from the coupling hole 20 of the protrusion 19. It can prevent becoming easy, and can improve durability reliably.
- the first coupling portion 20A and the fitting shaft portion 15A are coupled with each other only by an interference fit.
- the parts can be assembled with high accuracy due to the concentricity of the parts, and unlike the conventional screw structure, there is no deformation of the drive shaft 15 and no twisting of the threaded parts, and the assemblability is also good.
- the sleeve 30 is pressed against the stepped shoulder portion 18 provided on the drive shaft 15 by fitting the compressor impeller 13 to the drive shaft 15, and the compressor impeller 13 and the shoulder portion 18 are pressed. Is held in a state of receiving axial surface pressure. Therefore, the sleeve 30 is coupled to the drive shaft 15 and is not necessarily held in a state where it is subjected to the surface pressure, so that the compressor impeller 13 and the sleeve 30 are properly connected to the drive shaft 15.
- the sleeve 30 is configured to rotate integrally with the drive shaft 15 and a thrust collar 31 is disposed between the sleeve 30 and the shoulder 18. The thrust collar 31 is also clamped in a state of receiving a surface pressure, and is also fixed to the drive shaft 15 and rotates integrally.
- a thrust bearing 32 is disposed on the outer peripheral side of the contact portion 30B with the thrust collar 31 provided in the sleeve 30 so as to be sandwiched between the sleeve 30 and the thrust collar 31.
- the thrust bearing 32 has an annular shape through which the contact portion 30B can pass, and is fixed in a recessed space 16A provided in the housing 16. Unlike the horseshoe-shaped thrust bearing, the annular thrust bearing 32 can support the rotating surface of the sleeve 30 and the thrust collar 31 in a well-balanced manner over the entire circumference.
- the sleeve 30 is arranged so as to be accommodated in the recessed space 16A of the housing 16.
- the cylindrical portion 33 described above slightly protrudes from the recessed space 16A to the compressor impeller 13 side.
- a concave groove is provided over the entire circumference of the outer peripheral portion on the proximal end side of the cylindrical portion 33, and a pair of seal rings (seal means) 34 are fitted in the concave groove side by side in the axial direction. .
- the seal ring 34 is in contact with the holding ring 35 disposed in the recess space 16A so as to cover the thrust bearing 32, and seals the inside and outside of the recess space 16A.
- Lubricating oil power supplied to the thrust bearing 32 The seal ring 34 leaks from the recessed space 16A side to the compressor impeller 13 side. There is no worry of leaking.
- a retaining ring 36 is provided outside the retaining ring 35 to prevent the retaining ring 35 from being released from the recessed space 16A!
- a full float bearing 17 is arranged in the housing 16, and the drive shaft 15 integrated with the turbine wheel 14 is placed in the full float bearing 17 in the exhaust turbine. Insert 12 side force.
- a thrust collar 31 is inserted into the drive shaft 15 protruding from the recessed space 16A of the housing 16, and the thrust bearing 32, the retaining ring 35, and the locking ring 36 are sequentially disposed in the recessed space 16A. Insert the sleeve 30 into the drive shaft 15.
- the fitting shaft portion 15A of the drive shaft 15 is press-fitted into the coupling hole 20, and the cylindrical portion 33 is press-fitted into the outer peripheral surface of the protrusion 19 to be fitted. This completes the installation of the compression sign prop 13 into the turbocharger 1.
- the tip of the drive shaft 15 has a cylindrical shape, is press-fitted into the circular bottomed hole 20, and the cylindrical tubular portion 33 is fitted into the cylindrical protrusion 19. It was fixed together.
- the slip suppression means that suppresses slipping in the rotational direction at the connecting portion of the compressor impeller 13, the drive shaft 15, and the sleeve 30. 43, 46 and 49 are different.
- 4 shows a front view of the drive shaft 15
- FIG. 5 shows a front view of the sleeve 30,
- FIG. 6 shows a front view of the compressor impeller 13.
- the drive shaft 15 is provided with a male screw portion 41 at a portion to which the sleeve 30 is attached, and the sleeve 30 has a female screw portion 42 screwed with the male screw portion 41.
- Engraving The sleeve 30 is attached to the drive shaft 15 by screwing this portion, and the sleeve 30 is prevented from slipping or slipping around the drive shaft 15. That is, the first slip suppressing means 43 according to the present invention is formed by these screw portions 41 and 42.
- a two-sided width portion is formed by a pair of parallel flat surfaces 44 on the proximal end side of the outer peripheral portion of the protrusion 19.
- the cylindrical portion 33 is provided with a locking groove 45 that is locked to the flat surface 44.
- the locking groove 45 is locked to the flat surface 44, and the rotational slip between the cylindrical portion 33 and the protrusion 19 is suppressed.
- the second slip prevention means 46 is formed by the flat surface 44 and the locking groove 45.
- a two-sided width portion is formed by a pair of parallel flat surfaces 47 on the base end side of the fitting shaft portion 15 A, and the compressor
- the projection 19 of the impeller 13 is provided with a locking groove 48 that is locked to the flat surface 47.
- the locking groove 48 is locked to the flat surface 47, and the rotational slip between the drive shaft 15 and the protrusion 19 is suppressed.
- the third slip suppression means 49 is formed by the flat surface 47 and the locking groove 48.
- an engagement piece 51 protruding toward the tip side is provided at the tip of the drive shaft 15.
- This engagement piece 51 is provided at the back of the coupling hole 20 of the projection 19.
- the engagement hole 52 is inserted into the engagement hole 52 and engaged therewith. Also by the engagement of the engagement piece 51 and the engagement hole 52, the slip in the rotational direction is suppressed between the drive shaft 15 and the protrusion 19, and accordingly, the engagement piece 51 and the engagement hole 52 are suppressed. It can be said that the third slip prevention means 53 is formed in the present invention.
- FIG. 7A, FIG. 7B, FIG. 8A, and FIG. 8B show still another modified example of the drive shaft 15 and the sleeve 30 as the third embodiment of the present invention.
- the first slip suppression means 43 in the second embodiment is formed by the male thread portion 41 of the drive shaft 15 and the female thread portion 42 of the sleeve 30.
- Slip prevention means 56 is formed.
- the insertion portion 15B (the portion into which the sleeve 30 is inserted) of the drive shaft 15 has two parallel flat surfaces 54 on the proximal end side. A surface width portion is formed, and a locking groove 55 to be locked to the flat surface 54 is provided in the outer opening portion of the through hole 30A of the sleeve 30 shown in FIGS. 8A and 8B.
- the locking groove 55 is locked to the flat surface 54 so that the slip in the rotational direction is suppressed between the drive shaft 15 and the sleeve 30.
- the first slip suppression means 56 is formed by the flat surface 54 and the locking groove 55.
- the shape of other parts is substantially the same as in the second embodiment.
- the first slip restraining means in the force drive shaft 15 and the sleeve 30 provided with the first to third slip restraining means 43, 46, 49, 53, 56. 43 and 56, and if the third slip suppression means 49 and 53 are provided in the drive shaft 15 and the compressor impeller 13, slippage between the compressor impeller 13 and the sleeve 30 is inevitably caused. Therefore, the second slip suppression means 46 can be omitted.
- the force in which the tubular portion 33 is provided integrally with the sleeve 30 is provided integrally with the sleeve 30.
- a tubular portion 33 may be provided separately from the sleeve 30 as an annular tubular member.
- the material of the tubular member may be made to have a smaller linear expansion coefficient than the compressor impeller 13, and may be fitted and fitted to the protrusion 19.
- the present invention is used for turbochargers mounted on gasoline engines and diesel engines, as well as turboimpellers such as compressor impellers, turbo compressors, turbojets, turbo blowers, and turbo refrigerators that have a drive shaft for driving the compressor impeller it can.
- turboimpellers such as compressor impellers, turbo compressors, turbojets, turbo blowers, and turbo refrigerators that have a drive shaft for driving the compressor impeller it can.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006543007A JP4637853B2 (ja) | 2004-10-19 | 2005-10-18 | ターボ機械、ターボ機械に用いられるコンプレッサインペラ、及びターボ機械の製造方法 |
EP05795829A EP1803941A1 (en) | 2004-10-19 | 2005-10-18 | Turbo machine, compressor impeller used for turbo machine, and method of manufacturing turbo machine |
US11/665,232 US7909578B2 (en) | 2004-10-19 | 2005-10-18 | Turbo machine, compressor impeller used for turbo machine, and method of manufacturing turbo machine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004304473 | 2004-10-19 | ||
JP2004-304473 | 2004-10-19 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006043556A1 true WO2006043556A1 (ja) | 2006-04-27 |
Family
ID=36202971
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/019126 WO2006043556A1 (ja) | 2004-10-19 | 2005-10-18 | ターボ機械、ターボ機械に用いられるコンプレッサインペラ、及びターボ機械の製造方法 |
Country Status (6)
Country | Link |
---|---|
US (1) | US7909578B2 (ja) |
EP (1) | EP1803941A1 (ja) |
JP (1) | JP4637853B2 (ja) |
KR (1) | KR100861968B1 (ja) |
CN (1) | CN100476214C (ja) |
WO (1) | WO2006043556A1 (ja) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008298287A (ja) * | 2007-05-30 | 2008-12-11 | Nuovo Pignone Spa | 回転流体機械のロータ用の固定システム |
JP2011089459A (ja) * | 2009-10-22 | 2011-05-06 | Honda Motor Co Ltd | 過給機 |
WO2011114715A1 (ja) * | 2010-03-17 | 2011-09-22 | 東京電力株式会社 | 軸流圧縮機 |
JP2014173433A (ja) * | 2013-03-06 | 2014-09-22 | Shimadzu Corp | 真空ポンプ |
DE102017207259A1 (de) * | 2017-04-28 | 2018-10-31 | Continental Automotive Gmbh | Turbolader für eine Brennkraftmaschine, Turboladerläufer und Verdichterrad |
Families Citing this family (35)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101182122B1 (ko) * | 2008-04-08 | 2012-09-13 | 가부시키가이샤 아이에이치아이 | 터보 챠저 |
DE102008056058A1 (de) * | 2008-08-04 | 2010-02-11 | Mtu Friedrichshafen Gmbh | Abgasturbolader und Verfahren zur Montage eines solchen Abgasturboladers |
DE102008056059B4 (de) * | 2008-08-04 | 2010-11-18 | Mtu Friedrichshafen Gmbh | Abgasturbolader und Verfahren zur Montage eines Abgasturboladers |
DE102009015862A1 (de) * | 2009-04-01 | 2010-10-07 | Siemens Aktiengesellschaft | Getriebeverdichterrotor für Kaltgasanwendungen |
DE102009035629A1 (de) * | 2009-07-31 | 2011-02-17 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Ladevorrichtung, insbesondere Abgasturbolader für ein Kraftfahrzeug |
DE102009060056A1 (de) * | 2009-12-22 | 2011-06-30 | BorgWarner Inc., Mich. | Wellenverband eines Abgasturboladers |
WO2012112889A2 (en) | 2011-02-18 | 2012-08-23 | Ethier Jason | Fluid flow devices with vertically simple geometry and methods of making the same |
US8801379B2 (en) * | 2011-06-15 | 2014-08-12 | Honeywell International Inc. | Wheel and replaceable nose piece |
WO2013078115A1 (en) * | 2011-11-23 | 2013-05-30 | Borgwarner Inc. | Exhaust-gas turbocharger |
GB201122236D0 (en) * | 2011-12-23 | 2012-02-01 | Napier Turbochargers Ltd | Connector |
GB2498361A (en) * | 2012-01-10 | 2013-07-17 | Napier Turbochargers Ltd | Silicon carbide reinforced aluminium alloy turbocharger impeller |
WO2013106303A1 (en) * | 2012-01-13 | 2013-07-18 | Borgwarner Inc. | Sealing system and turbocharger incorporating the same |
CN104220714B (zh) * | 2012-04-24 | 2018-07-27 | 博格华纳公司 | 用于涡轮增压器的锥形凸台式止推轴承 |
DE112013002029T5 (de) * | 2012-05-16 | 2015-03-05 | Borgwarner Inc. | Schleuderscheiben-Öldichtung und Turbolader mit Schleuderscheiben-Öldichtung |
CN102767398A (zh) * | 2012-07-04 | 2012-11-07 | 联优机械(常熟)有限公司 | 透平膨胀机的叶轮与主轴的配合结构 |
GB201220300D0 (en) * | 2012-11-12 | 2012-12-26 | Cummins Ltd | Turbomachine bearing assembly preloading arrangement |
JP6333861B2 (ja) * | 2013-02-22 | 2018-05-30 | エコモーターズ,インコーポレーテッド | ターボ機械シャフトへの電気ロータの嵌合 |
US20140322019A1 (en) * | 2013-04-30 | 2014-10-30 | Dresser Inc. | Rotary element and compressor device comprised thereof |
DE102013213023A1 (de) | 2013-07-03 | 2015-01-08 | Continental Automotive Gmbh | Läufer für eine Turboladereinrichtung, Turboladereinrichtung mit einem Läufer und Welle für einen solchen Läufer |
CN105378247B (zh) * | 2013-07-26 | 2019-03-15 | 博格华纳公司 | 包括轴对称供给空腔的涡轮增压器吹扫密封件 |
US9664050B2 (en) | 2013-10-25 | 2017-05-30 | Ecomotors, Inc. | Bearings for a turbomachine having an electric motor |
JP6159418B2 (ja) * | 2013-12-11 | 2017-07-05 | 三菱重工業株式会社 | 回転体及び該回転体の製造方法 |
US20170074287A1 (en) * | 2014-03-11 | 2017-03-16 | Borgwarner Inc. | Compressor wheel-shaft assembly |
US10030580B2 (en) | 2014-04-11 | 2018-07-24 | Dynamo Micropower Corporation | Micro gas turbine systems and uses thereof |
FR3027070B1 (fr) | 2014-10-09 | 2019-08-02 | Cryostar Sas | Turbomachine tournant a des vitesses elevees |
EP3308000A4 (en) * | 2015-06-11 | 2019-05-01 | Eaton Corporation | REACH PLATE FOR TURBOCHARGER |
CN105863740A (zh) * | 2016-03-24 | 2016-08-17 | 中国北方发动机研究所(天津) | 高可靠性增压器涡轮转轴互锁式连接结构 |
DE102016119233A1 (de) * | 2016-10-10 | 2018-04-12 | Ihi Charging Systems International Gmbh | Laufzeug für einen Abgasturbolader und Abgasturbolader |
JP7187668B2 (ja) * | 2019-03-14 | 2022-12-12 | 三菱重工エンジン&ターボチャージャ株式会社 | コンプレッサホイール装置および過給機 |
CN110242354B (zh) * | 2019-05-28 | 2024-03-29 | 华电电力科学研究院有限公司 | 一种改进的高效径向透平分布式余压发电系统及其工作方法 |
US11401942B2 (en) | 2020-05-15 | 2022-08-02 | Garrett Transportation I Inc | Fastener arrangement for rotating group of turbomachine |
US11674406B2 (en) | 2021-08-06 | 2023-06-13 | Pratt & Whitney Canada Corp. | Variable gap between impeller rotor and static structure |
US11719243B2 (en) * | 2021-08-06 | 2023-08-08 | Pratt & Whitney Canada Corp. | Impeller rotor configured with wear resistant seal land |
US20230323874A1 (en) * | 2022-04-12 | 2023-10-12 | Delphi Technologies Ip Limited | Fluid pump with thrust bearing driver |
US20240159244A1 (en) * | 2022-11-16 | 2024-05-16 | Emerson Climate Technologies, Inc. | Foil bearing and driveshaft assemblies and compressor including same |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5030110A (ja) * | 1973-04-06 | 1975-03-26 | ||
JP2794338B2 (ja) * | 1989-10-30 | 1998-09-03 | アライド・シグナル・インコーポレーテツド | 孔なしハブコンプレツサホイールを備えるターボチヤージヤコンプレツサホイール装置 |
WO2003093651A1 (de) * | 2002-05-06 | 2003-11-13 | Abb Turbo Systems Ag | Befestigungsvorrichtung für ein laufrad auf einer welle |
EP1394387A2 (en) * | 2002-08-24 | 2004-03-03 | ALSTOM (Switzerland) Ltd | Turbochargers |
JP2004090130A (ja) * | 2002-08-30 | 2004-03-25 | Mitsubishi Heavy Ind Ltd | TiAl基合金と鋼材の接合方法 |
JP2004144095A (ja) * | 2002-10-24 | 2004-05-20 | Holset Eng Co Ltd | 圧縮機羽根車アセンブリ |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS48100205U (ja) * | 1972-02-28 | 1973-11-26 | ||
US4340317A (en) * | 1981-05-07 | 1982-07-20 | Northern Research & Engineering Corp. | Splineless coupling means |
JPS6026197A (ja) * | 1983-07-21 | 1985-02-09 | Asahi Glass Co Ltd | タ−ボ機械とそのための翼車片 |
JPS6023220U (ja) * | 1983-07-22 | 1985-02-18 | トヨタ自動車株式会社 | タ−ボチャ−ジャ用ロ−タ |
JPS611693U (ja) * | 1984-06-11 | 1986-01-08 | 日産自動車株式会社 | 圧縮機インペラ |
JPH0216079Y2 (ja) * | 1985-03-19 | 1990-05-01 | ||
JPS6326701U (ja) * | 1986-08-05 | 1988-02-22 | ||
JP2815697B2 (ja) * | 1990-10-31 | 1998-10-27 | 日本特殊陶業株式会社 | 過給機およびタービン羽車体 |
US5176497A (en) * | 1991-01-22 | 1993-01-05 | Allied-Signal Inc. | Boreless hub compressor wheel assembly for a turbocharger |
US5193989A (en) * | 1991-07-19 | 1993-03-16 | Allied-Signal Inc. | Compressor wheel and shaft assembly for turbocharger |
JPH0521200U (ja) * | 1991-09-02 | 1993-03-19 | 株式会社神戸製鋼所 | 遠心圧縮機用ロータ |
US6116855A (en) * | 1998-07-27 | 2000-09-12 | Hypro Corporation | Flexible impeller removal system |
JP2003139156A (ja) * | 2001-11-05 | 2003-05-14 | Kawasaki Heavy Ind Ltd | 組立回転体およびその締結機構 |
US6896479B2 (en) * | 2003-04-08 | 2005-05-24 | General Motors Corporation | Turbocharger rotor |
US7052241B2 (en) * | 2003-08-12 | 2006-05-30 | Borgwarner Inc. | Metal injection molded turbine rotor and metal shaft connection attachment thereto |
-
2005
- 2005-10-18 US US11/665,232 patent/US7909578B2/en not_active Expired - Fee Related
- 2005-10-18 WO PCT/JP2005/019126 patent/WO2006043556A1/ja active Application Filing
- 2005-10-18 CN CNB2005800351736A patent/CN100476214C/zh not_active Expired - Fee Related
- 2005-10-18 JP JP2006543007A patent/JP4637853B2/ja not_active Expired - Fee Related
- 2005-10-18 KR KR1020077008899A patent/KR100861968B1/ko not_active IP Right Cessation
- 2005-10-18 EP EP05795829A patent/EP1803941A1/en not_active Withdrawn
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5030110A (ja) * | 1973-04-06 | 1975-03-26 | ||
JP2794338B2 (ja) * | 1989-10-30 | 1998-09-03 | アライド・シグナル・インコーポレーテツド | 孔なしハブコンプレツサホイールを備えるターボチヤージヤコンプレツサホイール装置 |
WO2003093651A1 (de) * | 2002-05-06 | 2003-11-13 | Abb Turbo Systems Ag | Befestigungsvorrichtung für ein laufrad auf einer welle |
EP1394387A2 (en) * | 2002-08-24 | 2004-03-03 | ALSTOM (Switzerland) Ltd | Turbochargers |
JP2004090130A (ja) * | 2002-08-30 | 2004-03-25 | Mitsubishi Heavy Ind Ltd | TiAl基合金と鋼材の接合方法 |
JP2004144095A (ja) * | 2002-10-24 | 2004-05-20 | Holset Eng Co Ltd | 圧縮機羽根車アセンブリ |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008298287A (ja) * | 2007-05-30 | 2008-12-11 | Nuovo Pignone Spa | 回転流体機械のロータ用の固定システム |
JP2011089459A (ja) * | 2009-10-22 | 2011-05-06 | Honda Motor Co Ltd | 過給機 |
WO2011114715A1 (ja) * | 2010-03-17 | 2011-09-22 | 東京電力株式会社 | 軸流圧縮機 |
JP2011196188A (ja) * | 2010-03-17 | 2011-10-06 | Tokyo Electric Power Co Inc:The | 軸流圧縮機 |
US9188135B2 (en) | 2010-03-17 | 2015-11-17 | Tokyo Electric Power Company, Incorporated | Axial flow compressor |
JP2014173433A (ja) * | 2013-03-06 | 2014-09-22 | Shimadzu Corp | 真空ポンプ |
DE102017207259A1 (de) * | 2017-04-28 | 2018-10-31 | Continental Automotive Gmbh | Turbolader für eine Brennkraftmaschine, Turboladerläufer und Verdichterrad |
Also Published As
Publication number | Publication date |
---|---|
KR100861968B1 (ko) | 2008-10-07 |
EP1803941A1 (en) | 2007-07-04 |
KR20070064347A (ko) | 2007-06-20 |
US20070292268A1 (en) | 2007-12-20 |
JP4637853B2 (ja) | 2011-02-23 |
US7909578B2 (en) | 2011-03-22 |
JPWO2006043556A1 (ja) | 2008-05-22 |
CN100476214C (zh) | 2009-04-08 |
CN101040121A (zh) | 2007-09-19 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2006043556A1 (ja) | ターボ機械、ターボ機械に用いられるコンプレッサインペラ、及びターボ機械の製造方法 | |
US6896479B2 (en) | Turbocharger rotor | |
CA2354818C (en) | Turbocharger rotor with alignment couplings | |
JP4755071B2 (ja) | 排気ターボ過給機 | |
KR100923189B1 (ko) | 과급기 | |
US6899520B2 (en) | Methods and apparatus to reduce seal rubbing within gas turbine engines | |
CN103154471B (zh) | 排气涡轮增压器 | |
EP3608522B1 (en) | Turbocharger | |
US10662965B2 (en) | Sealing structure and turbocharger | |
JP2011137379A (ja) | インペラ取付構造及び過給機 | |
JP2020527661A (ja) | 排気ガス過給機のための結合具及び排気ガス過給機 | |
JP2020526695A (ja) | 排気ガス過給機のための結合具及び排気ガス過給機 | |
WO2022264313A1 (ja) | コンプレッサホイールの取付構造および過給機 | |
JP2020118061A (ja) | 回転機械のケーシング及び回転機械 | |
JP2005330816A (ja) | ターボ機械およびターボ機械のコンプレッサインペラ | |
CN221002876U (zh) | 一种喷嘴环安装定位结构 | |
US11220927B2 (en) | Assembly for a turbomachine | |
JP5071345B2 (ja) | ロータ | |
JPH09242553A (ja) | ターボチャージャのセミフロートベアリング支持構造 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KM KP KR KZ LC LK LR LS LT LU LV LY MA MD MG MK MN MW MX MZ NA NG NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SM SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): GM KE LS MW MZ NA SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LT LU LV MC NL PL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
WWE | Wipo information: entry into national phase |
Ref document number: 2006543007 Country of ref document: JP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2005795829 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 11665232 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 200580035173.6 Country of ref document: CN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1020077008899 Country of ref document: KR |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWP | Wipo information: published in national office |
Ref document number: 2005795829 Country of ref document: EP |
|
WWP | Wipo information: published in national office |
Ref document number: 11665232 Country of ref document: US |